Temperature control system and temperature control method for vehicle

Abstract

The invention provides a temperature control system and a temperature control method for a vehicle, which can ensure the heating capability even if the external air temperature is low and a heat source is difficult to ensure. The vehicle temperature control system includes a refrigerant circuit and a heat medium circuit. The heat medium circuit is configured such that a low-pressure-side circuit including the low-pressure-side heat exchanger and a high-pressure-side circuit including the high-pressure-side heat exchanger can be set in parallel, and a series circuit including the low-pressure-side heat exchanger and the high-pressure-side heat exchanger arranged in series can be set. The temperature control system is provided with, as an operation mode using a series circuit, a compressor heat source mode in which a heat medium flowing out of the high-pressure-side heat exchanger flows into the low-pressure-side heat exchanger via the temperature control device, and then flows into the high-pressure-side heat exchanger through the outdoor heat exchanger bypass path.

Description

Technical Field

[0001] The invention relates to a temperature control system assembled on a vehicle and a temperature control method using the temperature control system. Background Art

[0002] In electric vehicles and hybrid vehicles that obtain driving force from engines and motors, when the heat source is easily insufficient, in addition to the air conditioning functions required by the vehicle, such as heating and cooling, dehumidification, and ventilation, thermal management and waste heat utilization of vehicle-mounted equipment such as batteries are required. In response to such requirements, in addition to heat pump systems, multiple systems have been used, such as systems including a cooler for cooling the battery and a heater for heating the battery, or systems that use a pump to transport water heated by waste heat from a radiator to a temperature control target.

[0003] As a vehicle thermal management system capable of integrating the thermal management of air conditioning and equipment, a system has been proposed, which comprises: a primary circuit in which a refrigerant circulates according to a refrigeration cycle; and a secondary circuit in which a heat medium (water, etc.) that performs heat exchange with the refrigerant in the primary circuit is transported to the vehicle-mounted equipment by a pump (for example, Patent Document 1).

[0004] The thermal management system described in Patent Document 1 includes: a first heating medium circuit, which is provided with an evaporator of a refrigerant circuit and a heating medium external air heat exchanger; and a second heating medium circuit, which is provided with a condenser of a refrigerant circuit and a heater core of a machine room air conditioning unit. The first heating medium circuit and the second heating medium circuit are switched between a non-connected state (non-connected mode) and a connected state (connected mode) assuming a low external air temperature by switching the flow paths by a first switching mechanism and a second switching mechanism. In the non-connected mode, the heat pump operates to extract the heat of the outside air to the heat medium of the second heat medium circuit. In the connected mode, the heat medium flowing out of the evaporator does not flow into the heat medium outside air heat exchanger, but merges with the heat medium flowing out of the condenser, and the heat medium flows into the evaporator and condenser in parallel. By connecting the first heat medium circuit and the second heat medium circuit, the heat medium is heated and provided for heating. Previous technical literature Patent Literature

[0005] Patent Document 1: Japanese Patent No. 6083304 Summary of the invention Technical issues to be solved by the invention

[0006] In the connection mode of Patent Document 1, the heating medium flowing out of the evaporator and the heating medium flowing out of the condenser are mixed, and the temperature becomes the intermediate temperature of the temperatures of the respective heating mediums before mixing, and then flows into the evaporator and the condenser. Therefore, it takes time for the temperature of the heating medium flowing out of the condenser to rise compared with the non-connection mode. In addition, since the flow rate of the heating medium flowing into the indoor heat exchanger is reduced, there is room for improvement in heating capacity. An object of the present invention is to provide a temperature control system and a temperature control method for a vehicle, which can ensure heating capacity even when it is difficult to ensure a heat source due to low outside air temperature. Means for solving technical problems

[0007] The present invention is a temperature control system for a vehicle, which comprises: a refrigerant circuit, including a compressor, a high-pressure side heat exchanger, a pressure reducing unit and a low-pressure side heat exchanger, configured so that the refrigerant can circulate according to a refrigeration cycle; and a heat carrier circuit, configured so that a heat carrier that performs heat exchange with the refrigerant can circulate. The heat carrier circuit includes: a high-pressure side heat exchanger, which allows the refrigerant to exchange heat with the heat carrier; a low-pressure side heat exchanger, which allows the refrigerant to exchange heat with the heat carrier; an outdoor heat exchanger, which allows the external air to exchange heat with the heat carrier; a temperature control device, which is equivalent to a temperature control object heated or cooled by the heat carrier, or is used to heat or cool the temperature control object; an outdoor heat exchanger bypass path, which allows the heat carrier to bypass the outdoor heat exchanger; and multiple flow path switching valves, which are configured to be able to switch the flow of the heat carrier. The heat medium circuit is constructed so that a low-pressure side circuit including a low-pressure side heat exchanger and a high-pressure side circuit including a high-pressure side heat exchanger can be set in parallel by switching the flow of the heat medium by at least one of a plurality of flow path switching valves, and is constructed so that a series circuit including a low-pressure side heat exchanger and a high-pressure side heat exchanger arranged in series can be set. The temperature control system has a compressor heat source mode as an operating mode using a series circuit. In the compressor heat source mode, the heat carrier flowing out of the high-pressure side heat exchanger flows into the low-pressure side heat exchanger through the temperature control device, and then flows into the high-pressure side heat exchanger through the outdoor heat exchanger bypass path.

[0008] Furthermore, the present invention can also be extended to a temperature control method for a vehicle. Effects of the Invention

[0009] In the compressor heat source mode, the heat carrier flows in the bypass path of the outdoor heat exchanger to avoid heat dissipation to the outside air, while receiving heat generated by the power of the compressor from the refrigerant and transferring it to the temperature control object. In the compressor heat source mode, the heat carrier flowing out of the high-pressure side heat exchanger flows into the low-pressure side heat exchanger, and then flows out of the low-pressure side heat exchanger and flows into the high-pressure side heat exchanger, so the high-pressure side heat exchanger and the low-pressure side heat exchanger are connected in series. According to this series connection, the temperature of the heat medium flowing out of the high-pressure side heat exchanger can be raised more quickly than when the heat medium flows into the high-pressure side heat exchanger and the low-pressure side heat exchanger in parallel. In addition, since the circulation amount of the heat medium in the temperature control device is large, the heat exchange amount between the heat medium and the temperature control object becomes large. Furthermore, in the compressor heat source mode, the heat carrier passing through the high-pressure side heat exchanger and the temperature control device dissipates heat to the refrigerant through the low-pressure side heat exchanger. Compared with the case where heat is absorbed from the outside air to the heat carrier, the low pressure of the refrigerant circuit rises, and the density of the refrigerant sucked into the compressor increases accordingly, thereby increasing the circulation flow rate of the refrigerant. The increase in the circulation flow rate of the refrigerant increases the heat exchange capacity, thereby improving the heating capacity. Thereby, even when it is difficult to secure a heat source due to low outside air temperature, heating capacity can be secured. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] Figure 1 1 is a circuit diagram showing the vehicle temperature control system according to the first embodiment (cooling mode). Figure 2 It is shown Figure 1 The diagram shows the operating status of the system in heat pump mode. Figure 3 It is shown Figure 1 A diagram showing the operating state of the system in the first heater mode. Figure 4 It is shown Figure 1 A diagram showing the operating state of the system in the second heater mode. Figure 5 This is a circuit diagram showing a vehicle temperature control system according to a first modification of the first embodiment (first heater mode). Figure 6 This is a circuit diagram showing a vehicle temperature control system according to a second modification of the first embodiment (second heater mode). Figure 7 This is a circuit diagram showing a vehicle temperature control system according to a third modified example of the first embodiment (second heater mode). Figure 8This is a circuit diagram showing a vehicle temperature control system according to a fourth modified example of the first embodiment (second heater mode). Fig. 9 This is a circuit diagram showing a vehicle temperature control system according to a fifth modification of the first embodiment (second heater mode). Fig.10 This is a circuit diagram showing a vehicle temperature control system according to a sixth modification of the first embodiment (dehumidification and heating mode). Fig.11 It is shown Fig.10 A diagram showing the operating state of the system in the second heater mode. Fig.12 1 is a circuit diagram showing a vehicle temperature control system according to a second embodiment (heat pump mode). Fig.13 It is shown Fig.12 A diagram showing the operating state of the system in the first heater mode. Fig.14 It is shown Fig.12 A diagram showing the operating state of the system in the second heater mode. Fig.15 This is a circuit diagram showing a vehicle temperature control system according to a first modification of the second embodiment (first heater mode). Fig.16 This is a circuit diagram showing a vehicle temperature control system according to a sixth modification of the second embodiment (dehumidification and heating mode). Fig.17 It is shown Fig.16 A diagram showing the operating state of the system in the second heater mode. Fig.18 This is a circuit diagram (second heater mode) showing a vehicle temperature control system according to a partial modification of a sixth modification of the second embodiment. Fig.19 1 is a circuit diagram showing a vehicle temperature control system according to a third embodiment (cooling mode). Fig. 20 It is shown Fig.19 The diagram shows the operating state of the system in the first dehumidification and heating mode. Fig.21 It is shown Fig.19 The diagram shows the operating state of the system in the second dehumidification and heating mode. Fig. 22 It is shown Fig.19 The diagram shows the operating status of the system in heat pump mode. Fig.23 It is shown Fig.19 A diagram showing the operating state of the system in the first heater mode. Fig.24 It is shown Fig.19 A diagram showing the operating state of the system in the second heater mode. Fig.25 It is shown Fig.19 The diagram shows the operating state of the system in the direct heating second heater mode. Fig.26 This is a circuit diagram showing a vehicle temperature control system according to a sixth modification of the third embodiment (second heater mode). Fig. 27 This is a circuit diagram (cooling mode) showing a vehicle temperature control system according to a seventh modification of the third embodiment. DETAILED DESCRIPTION

[0011] Hereinafter, embodiments of the present invention will be described with reference to the drawings. [First embodiment] Figure 1 The vehicle temperature control system 1 shown is installed in, for example, a vehicle not shown in the figure, such as an electric vehicle that does not have an engine but obtains the driving force for the vehicle from an electric motor for driving, or a so-called hybrid vehicle that obtains the driving force for the vehicle from an engine and an electric motor. In addition to the air conditioning functions such as heating and cooling, dehumidification, and ventilation of the cabin 8 where passengers sit, the temperature control system 1 is also responsible for thermal management and waste heat recovery of vehicle-mounted devices such as a battery device (power supply device), a driving motor, and heat-generating electronic devices installed in the vehicle. The act of adjusting to an appropriate temperature or humidity, or managing the vehicle-mounted devices to an appropriate temperature is generally referred to as "thermal management." The electric power stored in the vehicle-mounted battery device is supplied to the temperature control system 1 and the electric devices or electronic devices included in the vehicle-mounted devices. The vehicle-mounted battery device is charged from an external power supply when the vehicle is stopped.

[0012] 〔Overall structure〕 The temperature control system 1 comprises: a refrigerant circuit 10, which is configured to allow the refrigerant to circulate; a heat medium circuit 20, which is configured to allow the heat medium for performing heat exchange with the refrigerant to circulate; and a control device 7, which sets the temperature control system 1 to a specified operating mode and controls the operating state of the temperature control system 1 according to the operating mode. Furthermore, the temperature control system 1 can include, for example, a sensor that detects the outside air temperature, the temperature in the machine room 8 (room temperature), and the like.

[0013] The temperature control system 1 has a plurality of operation modes which are selected by an occupant or the control device 7 as described below. Cooling mode M1 ( Figure 1 ) Heat pump mode M2 ​​( Figure 2 ) ·1st heater mode M3-1 ( Figure 3 ) · Second heater mode M3-2 ( Figure 4 ) As described later, the temperature control system 1 can ensure heating capacity even when the outside air temperature is significantly lower than 0° C. by at least the second heater mode M3 - 2 .

[0014] The operating mode required by the temperature control system 1 varies depending on the region where the vehicle is used. For example, the temperature control system 1 may not have the cooling mode M1. In addition, the temperature control system 1 may also have Figures 1 to 4 The operating modes are other than the modes M1, M2, M3-1, and M3-2 shown respectively.

[0015] 〔Refrigerant circuit structure〕 like Figure 1 As shown in an example of the configuration in FIG. 1 , the refrigerant circuit 10 includes a compressor 11, a condenser 12, an expansion valve 13, and an evaporator 14. In the refrigerant circuit 10, the refrigerant circulates according to a refrigeration cycle. As the refrigerant sealed in the refrigerant circuit 10, a known appropriate single refrigerant or mixed refrigerant can be used. For example, as the refrigerant of this embodiment, HFC (Hydro Fluoro Carbon: hydrofluorocarbon) refrigerants such as R410A and R32, HFO (Hydro Fluoro Olefin: hydrofluoroolefin) refrigerants such as R1234ze and R1234yf, or hydrocarbon (HC: Hydrocarbon: hydrocarbon) refrigerants such as propane and isobutane can be used. In particular, as the refrigerant of this embodiment, R1234yf is preferably used.

[0016] When the above-mentioned fluorine-based or hydrocarbon-based refrigerants are used, a subcritical refrigeration cycle is constructed in which the refrigerant pressure on the high-pressure side does not exceed the critical pressure of the refrigerant. When carbon dioxide (CO2) is used as a refrigerant, a transition critical refrigeration cycle is formed in which the refrigerant pressure on the high-pressure side exceeds the critical pressure of the refrigerant. Even in this case, the following effect can be obtained, that is, the refrigerant dissipates heat through the high-pressure side heat exchanger as in the condenser 12 of the present embodiment, and the refrigerant absorbs heat through the low-pressure side heat exchanger as in the evaporator 14 of the present embodiment, so a refrigerant that forms a transition critical refrigeration cycle such as the carbon dioxide refrigerant can also be adopted in the refrigerant circuit 10.

[0017] The compressor 11 corresponds to an electric compressor including a motor driven by electric power supplied from a battery device (not shown). The compressor 11 adiabatically compresses the refrigerant sucked into a casing (not shown) by a compression mechanism and discharges the refrigerant. The condenser 12 exchanges heat between the refrigerant gas discharged from the compressor 11 and a heating medium. The expansion valve 13 (decompression unit) adiabatically expands the refrigerant flowing out of the condenser 12 by decompressing the refrigerant. As the expansion valve 13, an electronic expansion valve whose opening can be controlled based on a command from the control device 7 is preferably used. However, it is also permissible to use a temperature expansion valve or a capillary tube instead of the expansion valve 13.

[0018] The evaporator 14 exchanges heat between the refrigerant flowing out of the expansion valve 13 and a heating medium. The refrigerant evaporated by the evaporator 14 is sucked into the compressor 11. An accumulator (gas-liquid separator) (not shown) may be provided between the evaporator 14 and the compressor 11 .

[0019] A relatively high refrigerant pressure (high pressure) is applied to the condenser 12, and a relatively low refrigerant pressure (low pressure) is applied to the evaporator 14. The refrigerant circulates in the refrigerant circuit 10 based on the pressure difference between the high pressure and the low pressure. exist Figure 1 In FIG, the flow of the refrigerant on the low-pressure side is indicated by a thick solid line, and the flow of the refrigerant on the high-pressure side is indicated by a thick dotted line. Figure 2 The following is also the same.

[0020] The compressor 11 , the condenser 12 , the expansion valve 13 , the evaporator 14 , and refrigerant pipes connecting these elements can be installed outside the machine room 8 .

[0021] 〔Structure of the heat carrier circuit〕 The heating medium circuit 20 is configured to circulate a heating medium capable of exchanging heat with the refrigerant through the condenser 12 and the evaporator 14. The heating medium is used to cool or heat at least one temperature control object. One of the temperature control objects in this embodiment corresponds to the air in the machine room 8. The heating medium sealed in the heating medium circuit 20 is a liquid such as water or salt water that is maintained in a liquid phase and circulated in the heating medium circuit 20. Examples of the salt water include a mixed liquid of water and propylene glycol or a mixed liquid of water and ethylene glycol.

[0022] like Figure 1 As shown in an example of the structure, the heat carrier circuit 20 includes a condenser 12, an evaporator 14, a first pump 21 and a second pump 22, an outdoor heat exchanger 23, an outdoor heat exchanger bypass path 24, an indoor heat exchanger 25, a first switching valve 31 (two-way flow switching valve) as a plurality of flow path switching valves, a second switching valve 32 and a third switching valve 33, and piping 401~412.

[0023] In this embodiment, the first switching valve 31 and the second switching valve 32 are four-way valves, and the third switching valve 33 is equivalent to a three-way valve. Figure 1 In the cooling mode M1 shown, both the heating medium flowing out of the evaporator 14 and the heating medium flowing out of the condenser 12 flow through the first switching valve 31 . Here, in each operation mode, "the heat medium flowing out of the evaporator 14" refers to the heat medium after flowing out of the evaporator 14 until it flows into the evaporator 14 or the condenser 12. Similarly, "the heat medium flowing out of the condenser 12" refers to the heat medium after flowing out of the condenser 12 until it flows into the condenser 12 or the evaporator 14.

[0024] The heat medium circuit 20 may include a liquid storage tank (not shown) as a mechanism for bringing the suction side of the pumps 21 and 22 to atmospheric pressure. According to the liquid storage tank, even if the pressure of the heat medium increases due to volume expansion caused by the temperature increase of the heat medium, the suction side of the pumps 21 and 22 is maintained at atmospheric pressure, so that the heat medium is stably pressure-fed to the heat medium circuit 20. A liquid storage tank can be provided on each suction side of the pumps 21 and 22, but only one liquid storage tank connected to the pipes 401 and 406 can be provided. In this case, a valve for connecting only one of the pipes 401 and 406 to the liquid storage tank can be provided on the path connecting the pipes 401 and 406 to the liquid storage tank. By closing the valve when using the series circuit CC described later, it is possible to prevent the heat medium from moving due to the pressure difference through the connecting path.

[0025] The elements of the heat medium circuit 20 other than the indoor heat exchanger 25 , namely, the condenser 12 , the evaporator 14 , the first pump 21 , the second pump 22 , the outdoor heat exchanger 23 , the outdoor heat exchanger bypass path 24 and the first to third switching valves 31 to 33 can be arranged outside the machine room 8 .

[0026] A flow path through which a high-pressure refrigerant flows and a flow path through which a heating medium flows are formed in the condenser 12. The high-pressure refrigerant and the heating medium exchange heat by contacting the walls of the flow paths.

[0027] A flow path through which the low-pressure refrigerant flows and a flow path through which the heating medium flows are formed in the evaporator 14. The low-pressure refrigerant and the heating medium exchange heat by contacting the walls of the flow paths.

[0028] The heating medium circuit 20 preferably includes: a condenser bypass path 12A for allowing the heating medium to bypass the condenser 12; and an evaporator bypass path 14A for allowing the heating medium to bypass the evaporator 14. In this case, the heating medium circuit 20 preferably includes: a condenser flow rate regulating valve 12V configured to be able to adjust the flow rate ratio of the heating medium between the condenser 12 and the condenser bypass path 12A; and an evaporator flow rate regulating valve 14V configured to be able to adjust the flow rate ratio of the heating medium between the evaporator 14 and the evaporator bypass path 14A.

[0029] The condenser flow regulating valve 12V and the evaporator flow regulating valve 14V are both electric valves capable of controlling the opening based on the command from the control device 7, which are equivalent to three-way valves. In addition, the three-way valves as flow regulating valves can be replaced by two two-way valves capable of adjusting the flow rate or a single two-way valve capable of adjusting the flow rate. For example, one two-way valve can be arranged in the condenser bypass path 12A, and the other two-way valve can be arranged in the piping 410. Alternatively, a single two-way valve can be arranged in one of the condenser bypass path 12A and the piping 410. The evaporator flow rate regulating valve 14V is also the same as described above.

[0030] The condenser flow regulating valve 12V has ports connected to the first switching valve 31, the condenser 12, and the condenser bypass path 12A, respectively. According to the respective openings of the port on the condenser 12 side and the port on the condenser bypass path 12A side, the flow rate of the heat medium flowing in the condenser 12 and the flow rate of the heat medium flowing in the condenser bypass path 12A are adjusted to a predetermined ratio. The heat medium distributed from the piping 409 to the piping 410 and the condenser bypass path 12A merges at the terminal of the condenser bypass path 12A. One of the flow rate of the heat medium flowing in the condenser 12 and the flow rate of the heat medium flowing in the condenser bypass path 12A can be 0.

[0031] The evaporator flow regulating valve 14V has ports connected to the first switching valve 31, the evaporator 14, and the evaporator bypass path 14A, respectively. By means of the evaporator flow regulating valve 14V, the flow rate of the heat medium flowing in the evaporator 14 and the flow rate of the heat medium flowing in the evaporator bypass path 14A are adjusted to a predetermined ratio, similarly to the above-mentioned condenser flow regulating valve 12V. The heat medium distributed from the pipe 404 to the pipe 405 and the evaporator bypass path 14A merges at the terminal of the evaporator bypass path 14A. One of the flow rate of the heat medium flowing in the evaporator 14 and the flow rate of the heat medium flowing in the evaporator bypass path 14A can be 0.

[0032] The first pump 21 and the second pump 22 are both equivalent to electric pumps driven by a motor (not shown). The motors connected to the first pump 21 and the second pump 22 are driven by electric power supplied from a battery device (not shown). The first pump 21 is provided on the pipe 401 connecting the evaporator 14 and the second switching valve 32. The first pump 21 sucks in and discharges the heating medium flowing out of the evaporator 14 to pressure-feed the heating medium. The second pump 22 is provided on the pipe 406 connecting the condenser 12 and the third switching valve 33. The second pump 22 sucks in and discharges the heating medium flowing out of the condenser 12 to pressure-feed the heating medium.

[0033] The outdoor heat exchanger 23 exchanges heat between the outside air outside the machine room 8 and the heat medium. The outdoor heat exchanger 23 is equivalent to a radiator arranged near the air inlet of the vehicle, for example. The outdoor blower 23A is equivalent to an electric blower that blows the outdoor air toward the outdoor heat exchanger 23. The outdoor air supplied to the outdoor heat exchanger 23 by the running of the vehicle and the operation of the outdoor blower 23A dissipates heat or absorbs heat according to the temperature difference between the outdoor air and the heat medium.

[0034] The outdoor heat exchanger bypass 24 allows the heat medium to bypass the outdoor heat exchanger 23. The outdoor heat exchanger bypass 24 of this embodiment bypasses the outdoor heat exchanger 23 from the position of the second switching valve 32 and is connected to the pipe 409 between the condenser flow rate regulating valve 12V and the first switching valve 31.

[0035] The indoor heat exchanger 25 exchanges heat between the air sent by the indoor blower 25A and the heat medium to supply conditioned air into the machine room 8. The indoor blower 25A corresponds to an electric blower that blows the air in the machine room 8 (inside air) or outside air toward the indoor heat exchanger 25. The HVAC (Heating, Ventilation, and Air Conditioning) unit U includes an indoor heat exchanger 25, an indoor blower 25A, and a duct (not shown) through which the air sent by the indoor blower 25A flows.

[0036] By switching the flow of the heating medium by at least one of the first to third switching valves 31 , 32 , 33 , the heating medium circuit 20 is configured to be able to set the low-pressure circuit C1 and the high-pressure circuit C2 in parallel and to be able to set the series circuit CC.

[0037] The high-pressure circuit C2 of the heat medium flowing out of the condenser 12 and returning to the condenser 12 is separated from the low-pressure circuit C1 flowing out of the evaporator 14 and returning to the evaporator 14. Hereinafter, the low-pressure circuit C1 and the high-pressure circuit C2 may be referred to as parallel circuits C1 and C2. When setting the parallel circuits C1 and C2, for example, Figure 1 As shown in the figure, both the heat medium flowing out of the condenser 12 and the heat medium flowing out of the evaporator 14 flow through the first switching valve 31, but inside the first switching valve 31, a flow path for the heat medium flowing out of the condenser 12 and another flow path for the heat medium flowing out of the evaporator 14 are provided. In the second switching valve 32 of the present embodiment, only the heat medium flowing out of the evaporator 14 flows. In the third switching valve 33 of the present embodiment, only the heat medium flowing out of the condenser 12 flows.

[0038] That is, the heat medium flowing out of the condenser 12 and the heat medium flowing out of the evaporator 14 do not flow simultaneously in the same flow path of any of the same switching valves among the plurality of switching valves 31 to 33. In the heat medium circuit 20, there is no pipe connection portion where the heat medium flowing out of the condenser 12 and the heat medium flowing out of the evaporator 14 merge, so the heat medium of the high-pressure side circuit C2 including the condenser 12 and the heat medium of the low-pressure side circuit C1 including the evaporator 14 do not mix with each other.

[0039] In the parallel circuit C1, C2 Figure 1 and Figure 2 In the figure, the flow of the relatively low temperature heat carrier (low temperature heat carrier) circulating in the low pressure side circuit C1 is indicated by a solid line, and the flow of the relatively high temperature heat carrier (high temperature heat carrier) circulating in the high pressure side circuit C2 is indicated by a single dotted line. At this time, from position A to position B on the heat carrier circuit 20, only the low temperature heat carrier flows, and from position C to position D, only the high temperature heat carrier flows. The path where neither the low temperature heat carrier nor the high temperature heat carrier is pressure-fed is indicated by a dotted line.

[0040] On the other hand, the series circuit CC is equivalent to a continuous circuit including the evaporator 14 and the condenser 12 arranged in series. When setting the series circuit CC, for example, Figure 4 As shown, the heat transfer medium flowing out of the condenser 12 flows into the evaporator 14 and then flows into the condenser 12 . In the series circuit CC Figure 3 and Figure 4 In the figure, the flow of a relatively low temperature heat carrier is represented by a solid line, and the flow of a relatively high temperature heat carrier is represented by a dashed line. Figure 4 Unlike the case where the parallel circuits C1 and C2 are provided, the flow of the heat medium from the evaporator 14 to the condenser 12 is indicated by a solid line, and the flow of the heat medium from the condenser 12 to the evaporator 14 is indicated by a dashed line. This means that if the heat medium flows into the evaporator 14, the temperature of the heat medium decreases due to heat dissipation to the refrigerant, and if the heat medium flows into the condenser 12, the temperature of the heat medium increases due to heat absorption from the refrigerant.

[0041] When the series circuit CC is set, the heat medium circulates in the condenser 12 and the evaporator 14 while repeating the temperature rise based on the condenser 12 and the temperature drop based on the evaporator 14. At this time, a continuous loop is formed in the heat medium circuit 20, so the heat medium can be pumped by only at least one of the first pump 21 and the second pump 22. That is, since it is possible to stop any one of the first pump 21 and the second pump 22, it is assumed that when the temperature control system 1 does not have an operation mode using the parallel circuits C1 and C2, only one of the first pump 21 and the second pump 22 is required. Furthermore, even in the operation mode using the series circuit CC, by operating the two pumps 21 and 22 , a sufficient circulation flow rate of the heating medium in the heating medium circuit 20 can be obtained.

[0042] When both parallel circuits C1 and C2 are used, the heat medium circuit 20 needs to have two pumps 21 and 22. The first pump 21 presses the heat medium in the low-pressure circuit C1, and the second pump 22 presses the heat medium in the high-pressure circuit C2.

[0043] The first to third switching valves 31 to 33 are all electric valves that can be controlled to open and close based on a command from the control device 7 , and are configured to be able to switch the flow path of the heating medium. The first switching valve 31 has ports connected to the condenser 12 , the evaporator 14 , the outdoor heat exchanger 23 , and the indoor heat exchanger 25 , respectively. The second switching valve 32 has ports connected to the evaporator 14 , the outdoor heat exchanger 23 , the outdoor heat exchanger bypass path 24 , and the indoor heat exchanger 25 , respectively. The third switching valve 33 has ports connected to the condenser 12 , the outdoor heat exchanger 23 , and the indoor heat exchanger 25 , respectively.

[0044] In order to set a path required for realizing a desired operation mode in the heating medium circuit 20 , the first to third switching valves 31 to 33 can be replaced with electric valves having an appropriate structure and an appropriate number.

[0045] The control device 7 can drive and control the rotation speed of the compressor 11 according to the heat load, and can increase or decrease the cooling capacity or heating capacity by increasing or decreasing the circulation flow rate of the refrigerant. In addition, the control device 7 detects physical quantities related to the room temperature, such as the room temperature, external air temperature, heating medium temperature, refrigerant temperature or pressure, etc. through sensors, and performs feedback control on the rotation speed of the compressor 11 to eliminate the deviation between the detected value and the target value, thereby adjusting the room temperature to the target temperature.

[0046] [Explanation of operation mode] Next, the operation of the temperature control system 1 will be described for each operation mode. (Parallel circuit operation mode) Cooling mode M1( Figure 1 ): In the heating medium circuit 20, a circuit corresponding to the cooling mode M1 is set based on the control instructions for the first to third switching valves 31 to 33, the condenser flow regulating valve 12V, and the evaporator flow regulating valve 14V. In the cooling mode M1, the outdoor heat exchanger bypass path 24 is not used, so the port corresponding to the second switching valve 32 is closed. Similarly, in other operation modes, circuits corresponding to the respective modes are provided.

[0047] The compressor 11, the first pump 21, the second pump 22, the outdoor blower 23A, and the indoor blower 25A are driven by electric power supplied from a battery device (not shown). Unless otherwise specified, the other operation modes are basically the same.

[0048] Regardless of the operation mode, only the heating medium flowing out of the evaporator 14 flows through the second switching valve 32 . Only the heating medium flowing out of the condenser 12 flows through the third switching valve 33 .

[0049] In cooling mode M1, the temperature control system 1 operates using parallel circuits C1 and C2. The heat medium (low-temperature heat medium) flowing out from the evaporator 14 to the piping 401 flows in the piping 402 along the flow path set inside the second switching valve 32 as shown by the solid arrow, and flows into the indoor heat exchanger 25. The air delivered to the indoor heat exchanger 25 by the indoor blower 25A absorbs heat from the heat medium and is blown out from the duct, thereby cooling the interior of the machine room 8. The heat medium that has absorbed heat from the air flows in the piping 403, and flows out to the piping 404 according to the flow path set inside the first switching valve 31, and returns to the evaporator 14. exist Figure 1 and Figure 2 In the illustrated example, due to the flow rate adjustment by the evaporator flow rate adjustment valve 14V, the entire amount of the heating medium flowing through the pipe 404 does not flow into the evaporator bypass path 14A but flows into the evaporator 14 through the pipe 405 .

[0050] On the other hand, the heat medium (high temperature heat medium) flowing out from the condenser 12 to the pipe 406 flows through the pipe 407 along the flow path provided inside the third switching valve 33 as indicated by the single-dot chain arrow, and flows into the outdoor heat exchanger 23. The heat medium flowing in the outdoor heat exchanger 23 dissipates heat to the outside air sent by the outdoor blower 23A, and flows through the pipe 408. Then, it flows out to the pipe 409 along the flow path provided inside the first switching valve 31, and returns to the condenser 12. exist Figure 1 and Figure 2 In the illustrated example, due to the flow rate adjustment by the condenser flow rate adjustment valve 12V, the entire amount of the heating medium flowing through the pipe 409 does not flow into the condenser bypass path 12A but flows into the condenser 12 through the pipe 410 .

[0051] According to the cooling mode M1 , the refrigerant dissipates heat to the outside air via the heating medium, so that the temperature control system 1 can be stably operated while preventing the high pressure of the refrigerant circuit 10 from increasing.

[0052] Heat pump mode M2( Figure 2 ): The heat pump mode M2 ​​corresponds to a mode for heating the interior of the machine room 8 , and heat is heated in the machine room 8 by extracting heat from the outside air as a heat source to a high-temperature heating medium having a higher temperature than the outside air and transferring the heat to the machine room 8 .

[0053] In the heat pump mode M2 ​​, the temperature control system 1 also operates using the parallel circuits C1 and C2 . In the heat pump mode M2 ​​, in contrast to the cooling mode M1 , the high-temperature heat medium is supplied to the indoor heat exchanger 25 and the low-temperature heat medium is supplied to the outdoor heat exchanger 23 . That is, the low-temperature heat medium flowing out of the evaporator 14 flows into the outdoor heat exchanger 23 via the second switching valve 32 and the pipe 411 as shown by the solid arrow. The heat medium that absorbs heat from the outside air returns to the evaporator 14 via the first switching valve 31 and the evaporator flow control valve 14V. The refrigerant evaporates by absorbing heat from the heating medium flowing into the evaporator 14, and is sucked into the compressor 11. The refrigerant discharged from the compressor 11 condenses in the condenser 12 by dissipating heat to the heating medium, thereby raising the temperature of the heating medium.

[0054] As indicated by the dashed arrow, the high temperature heating medium flowing out of the condenser 12 flows into the indoor heat exchanger 25 via the third switching valve 33 and the pipe 412. The heating medium heated in the machine room 8 returns to the condenser 12 via the first switching valve 31 and the condenser flow control valve 12V.

[0055] The heat pump mode M2 ​​utilizes the outside air as part of the heat source, and can ensure heating capacity while suppressing an increase in the power of the compressor 11 or the pumps 21 and 22 even if the outside air temperature drops below freezing, for example, to about -10°C.

[0056] (Heater mode using series circuit) Next, the operation modes both using the series circuit CC, namely the first heater mode M3-1 and the second heater mode M3-2, are described. When the outside air temperature is significantly lower than 0°C, for example, when the outside air temperature drops below -20°C, the amount of heat that can be absorbed from the outside air to the heat medium by the above-mentioned heat pump mode M2 ​​is reduced, and the density of the refrigerant sucked into the compressor 11 is reduced, and the power of the compressor 11 becomes smaller. Even in this case, the second heater mode M3-2 can be used to perform heating operation using the compressor 11 as a heat source.

[0057] For example, assuming that the temperature control system 1 is started after the vehicle has been stopped for a long time, the first heater mode M3-1 and the second heater mode M3-2 are described. After the temperature control system 1 is started, the control device 7 preferably implements the first heater mode M3-1 before the second heater mode M3-2. In this way, the heating operation can be started in advance.

[0058] The second heater mode M3-2 uses the power of the compressor 11 to heat the temperature-controlled object. In order to avoid heat dissipation from the heating medium to the outside air, the heating medium is detoured from the outdoor heat exchanger 23 to the outdoor heat exchanger bypass path 24.

[0059] When the temperature control system 1 is started after the vehicle has been stopped for a long time, when the outside air temperature is significantly lower than 0°C, the temperature of the heating medium is also as low as the outside air temperature. Therefore, just after the temperature control system 1 is started, the refrigerant is cooled by the heating medium, so that the low pressure of the refrigerant circuit 10 drops, and the evaporation temperature of the refrigerant is lower than the outside air temperature. Therefore, when the temperature control system 1 is started, the heat absorbed from the outside air to the heating medium through the outdoor heat exchanger 23 is transferred to the refrigerant through the first heater mode M3-1, taking precedence over the heating in the machine room 8, thereby heating the refrigerant. Then, the low pressure of the refrigerant circuit 10 rises to a specified value, and the refrigerant circuit 10 operates stably, and the temperature control object can be heated by extracting heat from the power of the compressor 11 to the heating medium, so it can be transferred to the second heater mode M3-2.

[0060] The second heater mode M3-2 supplies heat corresponding to the supplied power to the temperature control object, similarly to a resistance heating electric heater, for example. Therefore, although it is called a "heater" mode, the name of the second heater mode M3-2 is not necessarily limited to this. The first heater mode M3 - 1 is a mode presupposing a transition to the second heater mode M3 - 2 , and therefore uses the same name as the second heater mode M3 - 2 , but the name of the first heater mode M3 - 1 is not necessarily limited thereto.

[0061] 1st heater mode M3-1 ( Figure 3 ): refer to Figure 3 , together with the specific flow of the heat medium, the function of the first heater mode M3-1 is described. In the first heater mode M3-1, in order to allow the heat medium to absorb heat from the outside air through the outdoor heat exchanger 23, the heat medium is made to flow into the outdoor heat exchanger 23. In addition, in order to give priority to the heating of the refrigerant over the heating in the machine room 8, the heat medium is not made to flow into the condenser 12, but to bypass the condenser bypass path 12A, thereby preventing the refrigerant from dissipating heat to the heat medium. Then, in the evaporator 14, the heat is dissipated from the heat medium to the refrigerant. Furthermore, in order to suppress heat exchange between the air and the heating medium in the indoor heat exchanger 25, it is preferable to stop the operation of the indoor air-sending fan 25A.

[0062] In the first heater mode M3 - 1 , since the heating medium is caused to bypass the condenser 12 , the pressure loss of the heating medium is smaller than when the heating medium flows through the condenser 12 .

[0063] The heating medium flowing out of the evaporator 14 flows into the outdoor heat exchanger 23 via the second switching valve 32, and absorbs heat from the outside air. Figure 3 The heating medium that has been heated by absorbing heat from the outside air is indicated by a dashed line in FIG. The heating medium flowing out of the condenser bypass path 12A flows into the indoor heat exchanger 25 via the third switching valve 33. However, since the indoor blower 25A is stopped, the heat exchange between the heating medium in the indoor heat exchanger 25 and the cold air that is not conditioned is suppressed. The heating medium flowing out of the indoor heat exchanger 25 returns to the evaporator 14 via the first switching valve 31 and the evaporator flow regulating valve 14V. Then, it dissipates heat to the refrigerant through the evaporator 14, becomes a low-temperature heating medium, and flows out of the evaporator 14.

[0064] The heat exchange between the heating medium and the refrigerant and the heat exchange between the heating medium and the air are suppressed from the outlet of the outdoor heat exchanger 23 through the condenser bypass path 12A and the indoor heat exchanger 25 to the inlet of the evaporator 14. The heating medium, which absorbs heat from the outside air, passes through the condenser bypass path 12A and the indoor heat exchanger 25, and transfers the heat to the evaporator 14 where the refrigerant flows.

[0065] When the vehicle is stopped in a state where the outside air temperature is very low and below freezing, the temperatures of the heating medium and the refrigerant drop to the same level as the outside air temperature. Therefore, by starting the temperature control system 1, the compressor 11 starts to start, and when the refrigeration cycle just starts, the refrigerant cools the heating medium. However, according to the first heater mode M3-1, the low pressure of the refrigerant circuit 10 gradually increases by continuously transferring the heat absorbed from the outside air to the heating medium to the refrigerant, and the evaporation temperature also increases. In this process, the temperature of the heating medium that exchanges heat with the refrigerant also increases.

[0066] If the temperature of the heating medium exceeds the outside air temperature, the heat absorption from the outside air is insufficient, so the control device 7 can make the temperature control system 1 shift to the second heater mode M3-2 when the heating medium approaches the outside air temperature. For example, when the temperature of the heating medium exceeds a threshold value T3 that is lower than the outside air temperature (for example, -20°C) by a predetermined temperature difference α, the system can shift to the second heater mode M3-2. The difference between the outside air temperature and the threshold value is determined by the temperature difference corresponding to the time required to switch the flow of the heating medium relative to the instruction to switch the operation mode, etc.

[0067] In order to increase the amount of heat input to the refrigerant in the first heater mode M3-1, the rotation speed of each motor of the first and second pumps 21 and 22 can be increased to, for example, the maximum rotation speed. In this way, in addition to the heat given to the refrigerant from the outside air via the heat medium, the heat corresponding to the power of the first and second pumps 21 and 22 can be given from the heat medium to the refrigerant, and the heat dissipation from the heat medium to the refrigerant is promoted by increasing the circulation flow of the heat medium, thereby promoting the transition of the refrigerant circuit 10 to stable operation. Therefore, the time required to transfer from the first heater mode M3-1 to the second heater mode M3-2 from the start can be suppressed, so that the heating in the machine room 8 can be started in advance.

[0068] exist Figure 3 In the first heater mode M3-1 shown, depending on the outside air temperature or the operating status, a small amount of heat medium is allowed to flow into the condenser 12 through the condenser flow regulating valve 12V, or a small amount of heat medium is allowed to flow into the evaporator bypass path 14A through the evaporator flow regulating valve 14V.

[0069] Second heater mode M3-2 ( Figure 4 ): Next, refer to Figure 4 , together with the specific flow of the heating medium, the second heater mode M3-2 is described. In the second heater mode M3-2, in order to prevent the heating medium from dissipating heat to the outside air, the heating medium is detoured from the outdoor heat exchanger 23 through the outdoor heat exchanger bypass path 24. At this time, the operation of the outdoor air blower 23A may also be stopped. The control device 7 sends instructions to the first switching valve 31, the second switching valve 32, the evaporator flow regulating valve 14V, the condenser flow regulating valve 12V, the outdoor fan 23A and the indoor fan 25A, sets the path corresponding to the second heater mode M3-2 to the heat carrier circuit 20, stops the operation of the outdoor fan 23A, and starts the operation of the indoor fan 25A. Furthermore, the control device 7 operates at least one motor of the pumps 21 and 22 at an appropriate rotation speed.

[0070] The heat medium that absorbs heat from the refrigerant in the condenser 12 flows into the indoor heat exchanger 25 via the third switching valve 33 to provide heating in the machine room 8. Then, the heat medium that flows out of the indoor heat exchanger 25 flows into at least the evaporator 14 and the evaporator 14 in the evaporator bypass path 14A via the first switching valve 31 and the evaporator flow regulating valve 14V to dissipate heat to the refrigerant. The heat medium flowing out of the evaporator 14 flows into the outdoor heat exchanger bypass path 24 from the second switching valve 32, and after merging with the pipe 409 between the first switching valve 31 and the condenser flow regulating valve 12V, flows into at least the condenser 12 and the condenser 12 in the condenser bypass path 12A, thereby absorbing heat from the refrigerant. After switching from the first heater mode M3-1 to the second heater mode M3-2, the flow rate of the heat medium flowing into the condenser 12 can be gradually increased through the condenser flow regulating valve 12V.

[0071] In the second heater mode M3-2, the heat medium receives heat generated by the power of the compressor 11 from the refrigerant and transmits it to the temperature control object while flowing in the outdoor heat exchanger bypass path 24 to avoid heat dissipation to the outside air. According to the second heater mode M3-2, since the system is operated without heat input and output with the outside air, the heating in the machine room 8 can be continued regardless of the outside air temperature.

[0072] exist Figure 4 In the second heater mode M3-2 shown, the high-temperature heat medium represented by the single-dot chain line passes through the first switching valve 31. On the other hand, the low-temperature heat medium represented by the solid line does not pass through the first switching valve 31 because the terminal 24A of the outdoor heat exchanger bypass path 24 is connected to the pipe 409 downstream of the first switching valve 31. In this way, unlike the case where both the low-temperature heat medium and the high-temperature heat medium pass through the first switching valve 31 (refrigeration mode M1 or heat pump mode M2), there will be no heat input and output due to indirect contact between heat mediums of different temperatures in the heat medium flowing through the inside of the first switching valve 31. Therefore, in the evaporator 14, the temperature difference between the refrigerant and the heat medium will not decrease, so the heating capacity can be ensured.

[0073] When the heating operation is selected by the operation of the occupant or by the temperature control system 1, the control device 7 can select the above-mentioned heat pump mode M2 ​​when the detected outside air temperature is higher than the threshold value T1 (for example, -10°C). In addition, the control device 7 determines whether the temperature of the heating medium flowing into the outdoor heat exchanger 23 is lower than the outside air temperature. If the heat pump mode M2 ​​is selected only when the temperature of the heating medium is lower than the outside air temperature, heat can be reliably absorbed from the outside air. Furthermore, if the detected outside air temperature is higher than threshold T2 (eg, -15°C) lower than threshold T1, control device 7 can select second heater mode M3-2, and if the outside air temperature is lower than threshold T2, control device 7 can select first heater mode M3-1.

[0074] If the detected outside air temperature is lower than the threshold value T1, and the temperature control system 1 is just started, the control device 7 does not need to compare the outside air temperature with the threshold value T2, and can select the first heater mode M3-1 before the second heater mode M3-2. Alternatively, the second heater mode M3-2 can be selected first just after startup when the outside air temperature is lower than the threshold value T1, and a predetermined threshold value is applied to the detected temperature of the heating medium or refrigerant, thereby determining whether to continue the second heater mode M3-2 or switch to the first heater mode M3-1.

[0075] When the first heater mode M3-1 is performed before the second heater mode M3-2, the control device 7 operates the temperature control system 1 in the first heater mode M3-1 while waiting for the refrigerant circuit 10 to reach a stable state position. For example, if the temperature of the heat carrier exceeds a specified threshold value T3, the operation mode can be switched from the first heater mode M3-1 for startup to the second heater mode M3-2 for a stable state.

[0076] In the above example, the outside air temperature or the temperature of the heating medium or refrigerant is used as the threshold value, but a physical quantity such as pressure in the same state as the state of the heating medium or refrigerant represented by the temperature threshold value may be used.

[0077] [Main effects based on this embodiment]

[0078] In the second heater mode M3-2 using the series circuit CC, since the condenser 12 and the evaporator 14 are connected in series, the temperature of the heating medium flowing out of the condenser 12 can be increased more quickly than when the heating medium flows in parallel into the condenser 12 and the evaporator 14. In addition, since the circulation amount of the heating medium in the indoor heat exchanger 25 is large, the amount of heat exchange between the heating medium and the air becomes large.

[0079] Furthermore, in the second heater mode M3-2, the heat medium passing through the condenser 12 and the indoor heat exchanger 25 dissipates heat to the refrigerant through the evaporator 14, so compared with the heat pump mode M2, the low pressure of the refrigerant circuit 10 increases, and the density of the refrigerant sucked into the compressor 11 increases accordingly, thereby increasing the circulation flow rate of the refrigerant. Since the heat exchange capacity is improved by the increase in the refrigerant circulation flow rate, the heating capacity can be improved, so that the temperature in the machine room 8 can reach the target temperature earlier.

[0080] According to the temperature control system 1, by providing at least the second heater mode M3-2, even when it is difficult to secure a heat source due to low outside air temperature, heating capacity can be secured while supplying power required for securing a heat source to the compressor 11 and the like.

[0081] In addition, by providing the first heater mode M3-1, when the outside air temperature is significantly lower than the freezing point, even if the refrigerant cools the heating medium immediately after the refrigeration cycle is started, the refrigerant can be heated by the heating medium absorbing heat from the outside air, thereby suppressing the drop in the low pressure of the refrigerant circuit 10. Therefore, the refrigerant circuit 10 can be transferred to a stable state in advance. Therefore, when the temperature control system 1 is started when the outside air temperature is significantly lower than 0°C, it starts from the first heater mode M3-1, and the operation mode is switched to the second heater mode M3-2 when the refrigerant circuit 10 is transferred to a stable state, thereby enabling the temperature control object to reach the target temperature earlier than when operating in the second heater mode M3-2 right after startup.

[0082] In the heating medium circuit 20 of the present embodiment, only three switching valves 31 to 33 are used in total, except for the flow regulating valves 12V and 14V. According to the temperature control system 1 of the present embodiment, by reducing the number of flow path switching valves of the heating medium circuit 20, the component cost, the cost required for piping connection, and the cost required for maintenance of the heating medium circuit 20 are reduced, and various operation modes can be realized while being simply configured.

[0083] Furthermore, in the second heater mode M3 - 2 , the temperature control system 1 of this embodiment can control the heating capacity to be constant or variable by adjusting the flow ratio of the heating medium in the evaporator 14 and the evaporator bypass path 14A by the evaporator flow control valve 14V.

[0084] For example, when the physical quantity p such as the pressure of the refrigerant flowing out of the evaporator 14 is less than a predetermined threshold value T4, the flow rates of the heating medium flowing in the evaporator 14 and the evaporator bypass path 14A are adjusted by the evaporator flow regulating valve 14V to increase the flow rate of the heating medium flowing into the evaporator 14. If the flow rate of the heating medium flowing in the evaporator 14 increases, the heat dissipation from the heating medium to the refrigerant increases, the low pressure of the refrigerant circuit 10 rises, and the refrigerant circulation flow rate increases, so that the heating capacity can be increased. On the other hand, when the physical quantity p is larger than a predetermined threshold value T4, the flow rates of the heating medium flowing through the evaporator 14 and the evaporator bypass path 14A can be adjusted by the evaporator flow regulating valve 14V to reduce the flow rate of the heating medium flowing into the evaporator 14. By increasing or decreasing the threshold value T4, the heating capacity can be increased or decreased to adjust the room temperature.

[0085] The following description will focus on matters different from the above-described embodiment. The same reference numerals are given to components already described.

[0086] [First Modification of First Embodiment] Figure 5 The vehicle temperature control system 1-1 shown in the figure has an indoor heat exchanger bypass path 26 for making the heating medium bypass the indoor heat exchanger 25, especially in the first heater mode M3-1. In order to make the heating medium flow into the indoor heat exchanger bypass path 26, a four-way valve is used as the third switching valve 33-1.

[0087] In the first heater mode M3-1, as described above, it is preferable to stop the operation of the indoor air blower 25A. However, the first heater mode M3-1 may be executed in a state where the indoor air blower 25A is operated by an operation of an occupant or the like. Therefore, when the first heater mode M3-1 is selected as the operation mode, the control device 7 sends a command to the second switching valve 32 to set the path of the heating medium so that the heating medium does not flow into the indoor heat exchanger 25 but flows into the indoor heat exchanger bypass path 26. In the indoor heat exchanger bypass path 26, air is not supplied from the indoor air blower 25A.

[0088] Therefore, according to the first modification of the first embodiment, regardless of the operating / stopping state of the indoor air-sending fan 25A, it is possible to avoid the heat medium that absorbs heat from the outside air from dissipating heat to the cold air in the machine room 8. Therefore, it is possible to suppress the low pressure drop when the outside air temperature is low, and to transfer the refrigerant circuit 10 to a stable state in advance.

[0089] [Second Modification of First Embodiment] Figure 6 The vehicle temperature control system 1-2 shown in the figure is a system in which the positions of the first pump 21 and the second pump 22 are changed from the above-mentioned embodiment ( Figure 4 The positions of the first pump 21 and the second pump 22 are changed so as to sandwich the first switching valve 31. Figure 6 The first pump 21 is provided in the piping 408 , and the second pump 22 is provided in the piping 403 .

[0090] like Figure 6 As shown, even if the positions of the first pump 21 and the second pump 22 are changed, all the operation modes M1, M2, M3-1, and M3-2 described in the above embodiment will operate normally. Figure 6In the second heater mode M3-2 shown, the first pump 21 is arranged in the unused section of the heating medium circuit, specifically, the section from the second switching valve 32 via the outdoor heat exchanger 23 to the first switching valve 31. Therefore, a command can be sent from the control device 7 to stop the operation of the first pump 21. That is, in the second heater mode M3-2, the heating medium of the heating medium circuit 20 is pressure-fed only by the second pump 22.

[0091] [Third Modification of First Embodiment] Figure 7 The vehicle temperature control system 1-3 shown in the figure is also a system in which the positions of the first pump 21 and the second pump 22 are changed from the above-mentioned embodiment ( Figure 4 The first pump 21 is provided in the piping 409, and the second pump 22 is provided in the piping 404. like Figure 7 As shown, even if the positions of the first pump 21 and the second pump 22 are changed, all the operation modes M1, M2, M3-1, and M3-2 described in the above embodiment will work normally. In any mode M1, M2, M3-1, and M3-2, the first pump 21 and the second pump 22 are also arranged in the section where the heat medium is pressed toward the condenser 12, the evaporator 14, the outdoor heat exchanger 23, and the indoor heat exchanger 25.

[0092] The respective positions of the first pump 21 and the second pump 22 are not limited to the example shown in the figure. Taking into account the path of the heat medium in each operating mode, the respective positions of the first pump 21 and the second pump 22 can be appropriately determined within the range in which the heat medium can be pressurized by at least one of the first pump 21 and the second pump 22.

[0093] [Fourth Modification of the First Embodiment] Figure 8 The illustrated vehicle temperature control system 1 - 4 adjusts the temperature of the battery device 6 as a second temperature control target in addition to cooling and heating the interior of the machine room 8 as a first temperature control target. The heating medium circuit 20 of the system 1 - 4 is configured to supply the relatively low-temperature heating medium flowing out of the evaporator 14 to the battery device 6 , and is configured to supply the relatively high-temperature heating medium flowing out of the condenser 12 to the battery device 6 .

[0094] Although not specifically shown, the battery device 6 includes a battery body as a battery, and a battery heat exchanger or heat dissipation member provided in the battery body as required. The battery heat exchanger is, for example, a heat exchanger that exchanges heat between a heating medium and air, and is provided together with a blower that blows air toward the battery body. The battery device 6 is preferably maintained within a predetermined temperature range in order to stabilize the output and charging efficiency of the battery body and suppress degradation. For example, the temperature of the battery device 6 is adjusted to an appropriate temperature by supplying a heating medium of an appropriate temperature to a battery heat exchanger, blowing temperature-controlled air to the battery body, or supplying a heating medium of an appropriate temperature to a pipe thermally coupled to the battery body.

[0095] The heating medium circuit 20 includes heat exchange paths 414 and 415 configured to enable the battery device 6 and the heating medium to exchange heat directly or indirectly via air or the like, and battery switching valves 34 and 35 as four-way valves that switch between opening and closing corresponding to the heat exchange paths 414 and 415, respectively. The first battery switching valve 34 is disposed, for example, between the first switching valve 31 and the evaporator flow regulating valve 14V. The first battery switching valve 34 can switch the flow path of the heating medium between a state in which the heating medium flows from the pipe 404 into the first heat exchange path 414 and is supplied to the battery device 6, and a state in which the heating medium does not flow into the first heat exchange path 414 but flows in the pipe 404 toward the evaporator 14.

[0096] The second battery switching valve 35 is, for example, disposed between the first switching valve 31 and the condenser flow regulating valve 12V. The second battery switching valve 35 can switch the flow path of the heating medium between a state in which the heating medium flows from the pipe 409 into the second heat exchange path 415 and is supplied to the battery device 6, and a state in which the heating medium does not flow into the second heat exchange path 415 but flows in the pipe 409 toward the condenser 12.

[0097] In cooling mode M1 and heat pump mode M2, a low-temperature heat medium flows between the first switching valve 31 where the first battery switching valve 34 is located and the evaporator flow regulating valve 14V, and a high-temperature heat medium flows between the first switching valve 31 where the second battery switching valve 35 is located and the condenser flow regulating valve 12V. In the second heater mode M3-2, contrary to the above, a high-temperature heat medium flows between the first switching valve 31 where the first battery switching valve 34 is located and the evaporator flow regulating valve 14V, and a low-temperature heat medium flows between the first switching valve 31 where the second battery switching valve 35 is located and the condenser flow regulating valve 12V.

[0098] Refer to the second heater mode M3-2. Figure 8 , two methods of adjusting the temperature of the battery device 6 are described. Mode 1: The high-temperature heat medium flowing out of the condenser 12 passes through the indoor heat exchanger 25 and the first switching valve 31, flows from the first battery switching valve 34 in the outgoing path 414A of the first heat exchange path 414, and is supplied to the battery device 6. The heat medium that has exchanged heat with the battery device 6 flows in the loop 414B and returns to the first battery switching valve 34, and flows toward the evaporator 14. In this example, the second heat exchange path 415 is not used.

[0099] Mode 2: Contrary to the first mode described above, the first heat exchange path 414 is not used, and the low-temperature heat medium flowing out of the evaporator 14 passes through the first switching valve 31, passes through the second battery switching valve 35, flows through the outgoing path 415A of the second heat exchange path 415, and is supplied to the battery device 6. In this case, the heat medium that has exchanged heat with the battery device 6 flows in the loop 415B, returns to the second battery switching valve 35, and flows toward the condenser 12.

[0100] The control device 7 can perform temperature adjustment in one of the first mode and the second mode, for example, based on the temperature of the battery device 6 and the target temperature of the battery device 6 .

[0101] In cooling mode M1( Figure 1 ) and heat pump mode M2( Figure 3 ) It is also possible to use either the low-temperature heat medium or the high-temperature heat medium for adjusting the temperature of the battery device 6, which is the same as the second heater mode M3-2.

[0102] In addition, the temperature control system 1 - 4 may include only one of the first battery switching valve 34 / first heat exchange passage 414 and the second battery switching valve 35 / second heat exchange passage 415 .

[0103] [Fifth Modification of the First Embodiment] Fig. 9 The vehicle temperature control system 1-5 shown is relative to Figure 8 In the fourth modification, an indoor heat exchanger bypass path 26 is added for allowing the heating medium to bypass the indoor heat exchanger 25.

[0104] By providing the indoor heat exchanger bypass path 26, in the heat pump mode M2 ​​and Fig. 9 In the second heater mode M3-2 shown in FIG. 1 , the heating medium is not supplied to the indoor heat exchanger 25, that is, the air conditioning in the machine room 8 is not performed, and only the temperature of the battery device 6 is adjusted. Fig. 9 The third switching valve 33 of the four-way valve shown is closed at a port communicating with the indoor heat exchanger 25 , and is opened at a port communicating with the indoor heat exchanger bypass path 26 .

[0105] The position of the terminal 24A of the outdoor heat exchanger bypass path 24-1 for making the heat medium detour from the outdoor heat exchanger 23 can be Figure 8 The position shown can also be Fig. 9 As shown, between the outdoor heat exchanger 23 and the first switching valve 31. In the latter case, even if the positions of the pumps 21 and 22 are changed to Figure 6 In the position shown, the first pump 21 can also be used in the second heater mode M3-2. Figure 6 In the case of the illustrated configuration, only the second pump 22 is used in the second heater mode M3-2.

[0106] [Sixth Modification of the First Embodiment] Fig.10 and Fig.11 The temperature control system 1-6 for a vehicle shown in the figure performs dehumidification and heating in the dehumidification and heating mode M4 based on the heat pump mode M2. Therefore, the temperature control system 1-6 includes a first heat exchanger 25-1 and a second heat exchanger 25-2 as two indoor heat exchangers. The first heat exchanger 25-1 is disposed on the upstream side (windward side) of the flow of air sent from the indoor air-sending device 25A, and the second heat exchanger 25-2 is disposed on the downstream side (leeward side) of the same flow of air.

[0107] exist Fig.10 In the dehumidification and heating mode M4 shown, the heating medium flowing out of the evaporator 14 and passing through the second switching valve 32 is supplied to the first heat exchanger 25 - 1 , and the heating medium flowing out of the condenser 12 and passing through the third switching valve 33 is supplied to the second heat exchanger 25 - 2 .

[0108] In the dehumidification and heating mode M4, the air sent from the indoor air blower 25A is cooled to below the dew point and dehumidified by heat exchange with the low-temperature heating medium flowing through the first heat exchanger 25-1, and then heated by heat exchange with the heating medium flowing through the second heat exchanger 25-2 and blown into the machine room 8. The temperature control system 1-6 includes pipes 416 and 417 for conveying the low-temperature heating medium to the first heat exchanger 25-1 in the dehumidification and heating mode M4.

[0109] Fig.11 The second heater mode M3-2 of the temperature control system 1-6 is shown. In the second heater mode M3-2, the heating medium flowing out of the condenser 12 is supplied to the second heat exchanger 25-2 to perform heating. At this time, no heating medium is supplied to the first heat exchanger 25-1. In the cooling mode M1 (not shown) of the temperature control system 1-6, cooling is performed by supplying the heating medium flowing out of the evaporator 14 to the first heat exchanger 25-1. At this time, no heating medium is supplied to the second heat exchanger 25-2.

[0110] The HVAC unit U preferably has an electric damper (not shown) that can adjust the opening of the flow rate of air introduced into the second heat exchanger 25-2. In particular, in the dehumidification heating mode M4, the ratio of the flow rate introduced into the second heat exchanger 25-2 relative to the overall flow rate of air passing through the first heat exchanger 25-1 is changed by adjusting the opening of the damper based on the control command, thereby adjusting the temperature of the air blown out from the HVAC unit U to the target temperature of the room temperature.

[0111] From the first to sixth modified examples of the first embodiment described above, two or more can be appropriately selected and combined.

[0112] [Second embodiment] Next, refer to Figure 12 to Figure 14 , a vehicle temperature control system 2 according to a second embodiment of the present invention will be described. Figures 1 to 4 ), the second switching valve 32 is arranged on the discharge side of the first pump 21, and the third switching valve 33 is arranged on the discharge side of the second pump 22. In contrast, in the second embodiment, the first switching valve 31 is arranged on the discharge side of the first pump 21 and the second pump 22. The positions of the first to third switching valves 31 to 33 are roughly reversed up and down on the paper relative to the first embodiment. The second switching valve 32 for switching the flow of the low-temperature heating medium is configured as a three-way valve in the second embodiment. The third switching valve 33 for switching the flow of the high-temperature heating medium is configured as a four-way valve in the second embodiment.

[0113] The temperature control system 2 of the second embodiment can also have the following operation modes similar to the temperature control system 1 of the first embodiment. Similar to the first embodiment, the cooling mode M1 and the heat pump mode M2 ​​are equivalent to the operation modes using the parallel circuits C1 and C2. The first heater mode M3-1 and the second heater mode M3-2 are equivalent to the operation modes using the series circuit CC. Cooling mode M1 (not shown) Heat pump mode M2 ​​( Fig.12 ) ·1st heater mode M3-1 ( Fig.13 ) · Second heater mode M3-2 ( Fig.14 )

[0114] The refrigerant circuit 10 and the heating medium circuit 20 of the second embodiment are configured substantially the same as those of the first embodiment. According to the temperature control system 2 of the second embodiment, the same effects as those of the first embodiment can be obtained according to the structures of the refrigerant circuit 10 and the heating medium circuit 20. The structures of the refrigerant circuit 10 and the heating medium circuit 20 are not described repeatedly.

[0115] Each operating mode is briefly described. Heat pump mode M2( Fig.12 ): exist Fig.12 In the heat pump mode M2 ​​shown, the high-temperature heat medium represented by the single-dot chain line flows in parallel with the flow in the high-pressure side circuit C2, and the low-temperature heat medium represented by the solid line flows in the low-pressure side circuit C1. In this mode M2, while absorbing heat from the outside air to the low-temperature heat medium, the heat transferred to the high-temperature heat medium is supplied to the machine room 8 through the refrigeration cycle maintained by the refrigerant circuit 10.

[0116] 1st heater mode M3-1 ( Fig.13 ): right Fig.13 The flow of the heating medium in the first heater mode M3-1 shown will be described. The heating medium flowing out of the evaporator 14 flows into the outdoor heat exchanger 23 via the first switching valve 31, and absorbs heat from the outside air. The heating medium flowing out of the outdoor heat exchanger 23 flows into the condenser bypass path 12A via the third switching valve 33, and further flows into the indoor heat exchanger 25 via the first switching valve 31. The indoor air blower 25A stops operating, thereby suppressing the heat exchange between the heating medium and the air in the indoor heat exchanger 25. The heating medium flowing out of the indoor heat exchanger 25 returns to the evaporator 14 via the second switching valve 32, and dissipates heat to the refrigerant and flows out of the evaporator 14.

[0117] Second heater mode M3-2 ( Fig.14 ): right Fig.14 The flow of the heating medium in the second heater mode M3-2 shown will be described. The heat medium that absorbs heat from the refrigerant through the condenser 12 flows into the indoor heat exchanger 25 through the first switching valve 31, and heats the inside of the machine room 8. The heat medium then flows into the evaporator 14 through the second switching valve 32, and dissipates heat to the refrigerant. Then, if the heat medium does not pass through the first switching valve 31 but flows into the outdoor heat exchanger bypass path 24, and then flows into the condenser 12 through the third switching valve 33, it absorbs heat from the refrigerant.

[0118] According to the temperature control system 2 of the second embodiment, the low pressure drop when the outside air temperature is low can be suppressed, the refrigerant circuit 10 can be transferred to the stable state in advance, and the heating capacity can be ensured while supplying the power required for ensuring the heat source to the compressor 11, etc. Furthermore, according to the second embodiment, the same effects as those of the first embodiment can be obtained.

[0119] The first to sixth modifications of the first embodiment described above are also applicable to the second embodiment. The first to sixth modifications described below correspond to the modifications of the first embodiment with the same numbers. Each modification of the second embodiment will be briefly described.

[0120] [First Modification of Second Embodiment] Fig.15 The temperature control system 2-1 for a vehicle shown in the figure has an indoor heat exchanger bypass path 26-2 for making a heating medium bypass the indoor heat exchanger 25. When the heating medium flows into the indoor heat exchanger bypass path 26-2, the port of the second switching valve 32-2 as a four-way valve communicating with the indoor heat exchanger bypass path 26-2 is opened, and the port of the second switching valve 32-2 communicating with the indoor heat exchanger 25 is closed. When the heating medium flows into the indoor heat exchanger 25, the opening and closing state of the port of the second switching valve 32-2 is switched to the opposite of the above.

[0121] By providing the indoor heat exchanger bypass path 26-2, regardless of the operating / stopping state of the indoor air-sending fan 25A, it is possible to prevent the heat medium that absorbs heat from the outside air from dissipating heat to the cold air in the machine room 8 in the operating state based on the first heater mode M3-1. Therefore, it is possible to suppress the low pressure drop when the outside air temperature is low, and to transfer the refrigerant circuit 10 to a stable state in advance.

[0122] [Second Modification of Second Embodiment] (illustration omitted) In the second embodiment ( Figure 12 to Figure 14 ) is also similar to the second variant of the first embodiment ( Figure 6 ) Similarly, the positions of the first pump 21 and the second pump 22 can be changed. Specifically, the first pump 21 can be provided in the pipe 407 and the second pump 22 can be provided in the pipe 402 so that the first switching valve 31 is interposed between the first pump 21 and the second pump 22 . In this case, Fig.14 In the second heater mode M3-2 shown, the first pump 21 is arranged in the unused section of the heating medium circuit, so the operation of the first pump 21 can be stopped. That is, in the second heater mode M3-2, the heating medium of the heating medium circuit 20 is pumped only by the second pump 22.

[0123] [Third Modification of Second Embodiment] (illustration omitted) Furthermore, it is also possible to combine with the third modification example ( Figure 7 ) Similarly, the positions of the first pump 21 and the second pump 22 are changed. Specifically, the first pump 21 can be provided in the pipe 404 , and the second pump 22 can be provided in the pipe 409 .

[0124] [Fourth Modification of Second Embodiment] (illustration omitted) The temperature control system 2 can include the fourth modification example ( Figure 8 )'s heat exchange paths 414, 415 and the battery switching valves 34, 35 have the same temperature adjustment mechanism.

[0125] In the second embodiment, the first battery switching valve 34 is disposed, for example, between the second switching valve 32 and the evaporator flow rate regulating valve 14V. The second battery switching valve 35 is disposed, for example, between the third switching valve 33 and the condenser flow rate regulating valve 12V.

[0126] For example, by switching the flow paths using battery switching valves 34 and 35 based on the temperature of the heat medium indicating the temperature of battery device 6 and the target temperature of battery device 6, the temperature of battery device 6 can be adjusted using either or both of a low-temperature heat medium and a high-temperature heat medium.

[0127] [Fifth Modification of the Second Embodiment] (illustration omitted) The temperature control system 2 may also include a temperature adjustment mechanism for the battery device 6 similarly to the fourth modification example described above, and may be different from the fifth modification example ( Fig. 9 ) is also provided with an indoor heat exchanger bypass path 26.

[0128] By providing the indoor heat exchanger bypass path 26 , in the heat pump mode M2 ​​and the second heater mode M3 - 2 , the heating medium is not supplied to the indoor heat exchanger 25 , that is, the air conditioning in the machine room 8 is not performed, and only the temperature of the battery device 6 can be adjusted.

[0129] [Sixth Modification of the Second Embodiment] Fig.16 and Fig.17 The temperature control system 2-6 shown is similar to the sixth variation of the first embodiment ( Fig.10 and Fig.11 As shown), the first heat exchanger 25-1 and the second heat exchanger 25-2 are provided as two indoor heat exchangers, and dehumidification and heating are performed by a dehumidification and heating mode M4 based on a heat pump mode M2.

[0130] exist Fig.16 In the dehumidification and heating mode M4 shown, the first heat exchanger 25-1 is supplied with the heating medium flowing out of the evaporator 14 and passing through the first switching valve 31, and the second heat exchanger 25-2 is supplied with the heating medium flowing out of the condenser 12. The temperature control system 2-6 includes pipes 416 and 417 for flowing the low-temperature heating medium to the first heat exchanger 25-1 in the dehumidification and heating mode M4.

[0131] In the dehumidification heating mode M4, the air delivered from the indoor fan 25A is cooled to below the dew point and dehumidified through heat exchange with the low-temperature heating medium flowing in the first heat exchanger 25-1, and then heated and blown into the machine room 8 through heat exchange with the heating medium flowing in the second heat exchanger 25-2.

[0132] Fig.17 The second heater mode M3-2 of the temperature control system 2-6 is shown. In the second heater mode M3-2, the heating medium flowing out of the condenser 12 is supplied to the second heat exchanger 25-2 to perform heating. At this time, the heating medium is not supplied to the first heat exchanger 25-1. The outdoor heat exchanger bypass path 24 is similar to the second embodiment ( Fig.14 The heat medium flowing out of the evaporator 14 does not flow through the first switching valve 31 but flows into the outdoor heat exchanger bypass path 24 and flows toward the condenser 12 in the second heater mode M3-2. In the second heater mode M3-2, neither the heat medium flowing out of the condenser 12 nor the heat medium flowing out of the evaporator 14 flows through the first switching valve 31.

[0133] In the cooling mode M1 (not shown) of the temperature control system 2-6, cooling is performed by supplying the heating medium flowing out of the evaporator 14 to the first heat exchanger 25-1. At this time, no heating medium is supplied to the second heat exchanger 25-2.

[0134] [Partial Changes to the Sixth Modification of the Second Embodiment] Fig.18 The temperature control system 2-7 shown is the same as the sixth variant ( Fig.16 and Fig.17 ) Similarly, dehumidification and heating are performed by the heat pump mode M2. The temperature control system 2-7 of the seventh modification is different from the temperature control system 2-6 of the sixth modification in that only a part of the path of the heating medium circuit 20 is different.

[0135] In the seventh modification, the outdoor heat exchanger bypass path 24 is connected to the discharge side of the first pump 21 via the first switching valve 31, so in the second heater mode M3-2, the heating medium flowing out of the evaporator 14 flows into the outdoor heat exchanger bypass path 24 through the first switching valve 31 and flows toward the condenser 12. At this time, only the heating medium flowing out of the evaporator 14 flows through the first switching valve 31 because the heating medium flowing out of the condenser 12 does not pass through. In this way, in the heating medium flowing inside the first switching valve 31, heat does not flow in and out due to indirect contact with the heating medium of different temperature, so heat loss can be suppressed.

[0136] From the first to sixth modified examples of the second embodiment described above, two or more can be appropriately selected and combined.

[0137] [Third Embodiment] Next, refer to Figures 19 to 25 Next, a vehicle temperature control system 3 according to a third embodiment of the present invention will be described. The temperature control system 3 includes a refrigerant heat exchanger 14 - 2 on the indoor side, and the refrigerant heat exchanger 14 - 2 supplies the refrigerant circulating in the refrigerant circuit 10 .

[0138] Compared with the refrigerant circuit 10 ( Figure 1 ) Similarly, the refrigerant circuit 10-3 of the temperature control system 3 comprises: a first refrigerant circuit R1, which is configured so that the refrigerant can circulate in the compressor 11, the condenser 12, the first expansion valve 13-1 as the first pressure reducing section, and the evaporator 14-1; and a second refrigerant circuit R2, which is configured so that the refrigerant can circulate in the compressor 11, the condenser 12, the second expansion valve 13-2 as the second pressure reducing section, and the refrigerant heat exchanger 14-2 as the evaporator.

[0139] The first refrigerant circuit R1 and the second refrigerant circuit R2 can each independently form a refrigeration cycle. When both the first refrigerant circuit R1 and the second refrigerant circuit R2 are used simultaneously, the expansion valves and evaporators of the first refrigerant circuit R1 and the second refrigerant circuit R2 are connected in parallel. The second refrigerant circuit R2 includes a pipe 501 connected to the refrigerant outflow side of the condenser 12 and a pipe 502 connected to the refrigerant discharge side of the evaporator 14 .

[0140] It is also acceptable to use a capillary tube instead of the expansion valves 13-1 and 13-2. In this case, in an operation mode in which one of the refrigerant circuits R1 and R2 is used, an on-off valve is required to close the capillary tube of the other refrigerant circuit that is not used.

[0141] In addition, the terminal 24A of the outdoor heat exchanger bypass path 24 is provided between the outdoor heat exchanger 23 and the first switching valve 31, but the present invention is not limited thereto. The terminal 24A of the outdoor heat exchanger bypass path 24 may also be provided between the outdoor heat exchanger 23 and the first switching valve 31. Figure 4 ) Similarly, it is set between the first switching valve 31 and the condenser 12.

[0142] The temperature control system 3 has, for example, the following plural operation modes. Cooling mode M1 ( Fig.19 ) ·1st dehumidification and heating mode M4-1 ( Fig. 20 ) · Second dehumidification and heating mode M4-2 ( Fig.21 ) Heat pump mode M2 ​​( Fig. 22 ) ·1st heater mode M3-1 ( Fig.23 ) · Second heater mode M3-2 ( Fig.24 and Fig.25 ) The heat pump mode M2 ​​, the first heater mode M3 - 1 , and the second heater mode M3 - 2 described above play the same role as the modes of the same name in the first embodiment.

[0143] The heating medium circuit 20 of the temperature control system 3 is configured similarly to the first embodiment ( Figure 1 ) is substantially the same as the heat medium circuit 20. However, the second switching valve 32 is changed from a four-way valve to a three-way valve.

[0144] The refrigerant heat exchanger 14-2 is disposed on the upwind side of the air flow generated by the indoor air-sending device 25A that sends air to the refrigerant heat exchanger 14-2 and the indoor heat exchanger 25. The indoor heat exchanger 25 is disposed on the downwind side of the air flow.

[0145] In the cooling mode M1, the first dehumidification and heating mode M4-1, the second dehumidification and heating mode M4-2, and the heat pump mode M2, the low-pressure side circuit C1 of the heating medium that flows into the evaporator 14 after flowing out of the evaporator 14 is separated from the high-pressure side circuit C2 of the heating medium that flows into the condenser 12 after flowing out of the condenser 12. However, in the cooling mode M1 and the first dehumidification and heating mode M4-1, the low-pressure side circuit C1 is not used. Therefore, the operation of the first pump 21 that pressurizes the heating medium in the low-pressure side circuit C1 can be stopped.

[0146] On the other hand, in the first heater mode M3 - 1 and the second heater mode M3 - 2 , since the series circuit CC is used, the heating medium flowing out of the condenser 12 flows into the evaporator 14 , flows out of the evaporator 14 , and flows into the condenser 12 .

[0147] [Explanation of operation mode] For each operation mode, the function of the temperature control system 3 is described. Cooling mode M1( Fig.19 ): The cooling mode M1 uses only the second refrigerant circuit R2 of the first refrigerant circuit R1 and the second refrigerant circuit R2. Therefore, the first expansion valve 13-1 of the first refrigerant circuit R1 is closed. Furthermore, in the cooling mode M1, only the high-pressure circuit C2 is used, and the low-pressure circuit C1 is not used. Therefore, the operation of the first pump 21 that pumps the heat medium in the low-pressure circuit C1 can be stopped.

[0148] The flow of the refrigerant in the second refrigerant circuit R2 is described. The refrigerant gas sucked into the compressor 11 is adiabatically compressed and discharged by the compressor 11, and is liquefied by heat exchange with the heat medium in the condenser 12. Furthermore, the refrigerant flows into the second expansion valve 13-2 through the piping 501, and adiabatically expands by the decompression based on the second expansion valve 13-2, and the refrigerant with a reduced temperature flows into the refrigerant heat exchanger 14-2. The refrigerant flowing in the refrigerant heat exchanger 14-2 cools the air delivered from the indoor blower 25A, thereby cooling the machine room 8. The refrigerant that has cooled the refrigerant heat exchanger 14-2 flows in the piping 502 and is sucked into the compressor 11.

[0149] As the flow of the heating medium, the heating medium of the high pressure side circuit C2 transfers heat received from the refrigerant to the outdoor heat exchanger 23 through the condenser 12. The heating medium that has transferred heat to the outside air through the outdoor heat exchanger 23 returns to the condenser 12 through the first switching valve 31.

[0150] According to the cooling mode M1 of the temperature control system 3, the temperature control object can be directly cooled without passing through a heat medium by the refrigerant supplied to the refrigerant heat exchanger 14-2 as an evaporator as a cold heat source. Therefore, the cooling capacity can be improved, and the followability of the control relative to the temperature change of the temperature control object or the outside air can also be improved.

[0151] 1st dehumidification and heating mode M4-1 ( Fig. 20 ): The first dehumidification and heating mode M4-1 is suitable for dehumidification and heating when the cooling load is relatively high as the air conditioning load. In the first dehumidification and heating mode M4-1, similarly to the cooling mode M1, the second refrigerant circuit R2 used in the first and second refrigerant circuits R1 and R2 uses the high-pressure side circuit C2 in the low-pressure side circuit C1 and the high-pressure side circuit C2.

[0152] The flow of the refrigerant in the second refrigerant circuit R2 is the same as that in the cooling mode M1. The heating medium of the high-pressure side circuit C2 flows through the first circuit L1 and the second circuit L2 which are paths connected in parallel to the condenser 12 . The flow of the heating medium in the first circuit L1 is the same as that in the cooling mode M1 . That is, the heating medium that absorbs heat from the refrigerant in the condenser 12 dissipates heat to the outside air in the outdoor heat exchanger 23 and returns to the condenser 12 .

[0153] The second circuit L2 flows from the condenser 12 into the indoor heat exchanger 25 via the third switching valve 33 , and returns to the condenser 12 via the first switching valve 31 . The air sent by the indoor blower 25A is cooled to a dew point or less by heat exchange with the refrigerant in the refrigerant heat exchanger 14 - 2 , and then heated by heat exchange with the heating medium in the indoor heat exchanger 25 , and is blown into the machine room 8 .

[0154] According to the first dehumidification and heating mode M4 - 1 , heat is dissipated to the outside air using the high-pressure side circuit C2 , so that air conditioning can be performed even when the cooling load is high.

[0155] Second dehumidification and heating mode M4-2 ( Fig.21 ): The second dehumidification and heating mode M4-2 is suitable for dehumidification and heating when the heating load is relatively high as the air conditioning load. In the second dehumidification and heating mode M4-2, both the first and second refrigerant circuits R1 and R2 are used, and both the low-pressure circuit C1 and the high-pressure circuit C2 are used.

[0156] The flow of the heating medium in the low-pressure circuit C1 and the high-pressure circuit C2 is consistent with the heat pump mode M2 ​​( Figure 2 ) is the same as the flow of the heat carrier under. The low-temperature heat medium in the low-pressure circuit C1 flows out of the evaporator 14 - 1 , flows into the outdoor heat exchanger 23 via the second switching valve 32 , absorbs heat from the outside air, and then returns to the evaporator 14 - 1 via the first switching valve 31 . When the high-temperature heating medium of the high-pressure side circuit C2 flows out of the condenser 12 , it flows into the indoor heat exchanger 25 via the third switching valve 33 , heats the air dehumidified by the refrigerant heat exchanger 14 - 2 , and then returns to the condenser 12 via the first switching valve 31 .

[0157] The first expansion valve 13 - 1 / evaporator 14 - 1 of the first refrigerant circuit R1 and the second expansion valve 13 - 2 / refrigerant heat exchanger 14 - 2 of the second refrigerant circuit R2 are connected in parallel. Therefore, the refrigerant discharged from the compressor 11 and dissipating heat to the heat medium through the condenser 12 flows into the first expansion valve 13-1 and the second expansion valve 13-2 respectively. The refrigerant flowing out of the first expansion valve 13-1 absorbs heat from the heat medium in the evaporator 14-1. On the other hand, the refrigerant flowing out of the second expansion valve 13-2 cools the air in the refrigerant heat exchanger 14-2. The compressor 11 sucks the refrigerant flowing out of the evaporator 14-1 and the refrigerant flowing out of the refrigerant heat exchanger 14-2.

[0158] According to the second dehumidification and heating mode M4 - 2 , heat is absorbed from the outside air by using the low-pressure side circuit C1 , so that air conditioning can be performed even when the heating load is high.

[0159] Heat pump mode M2( Fig. 22 ): The heat pump mode M2 ​​performs normal heating. In the heat pump mode M2, the first refrigerant circuit R1 is used, and both the low-pressure circuit C1 and the high-pressure circuit C2 are used. The second expansion valve 13 - 2 of the unused second refrigerant circuit R2 remains closed.

[0160] The flow of the heating medium in the low-pressure circuit C1 and the high-pressure circuit C2 is the same as that in the second dehumidification and heating mode M4-2. The heating medium that absorbs heat from the outside air through the low-pressure circuit C1 dissipates heat to the refrigerant in the evaporator 14. The refrigerant in the high-pressure circuit C2 absorbs heat from the refrigerant in the condenser 12 and is supplied to the indoor heat exchanger 25. The air sent by the indoor air blower 25A is heated by the heating medium, thereby heating the inside of the machine room 8.

[0161] 1st heater mode M3-1 ( Fig.23 ): The first heater mode M3 - 1 is suitable for when the temperature control system 3 is activated when the outside air temperature is significantly lower than 0° C. In the first heater mode M3 - 1 , the first refrigerant circuit R1 is used, and the series circuit CC of the heating medium circuit 20 is used.

[0162] The flow of the heating medium in the heating medium flow path 20 is different from the first heater mode M3-1 ( Figure 3 ) is the same as the flow of the heat carrier under. If the heating medium flowing out of the evaporator 14 absorbs heat from the outside air in the outdoor heat exchanger 23, it flows into the condenser bypass path 12A via the first switching valve 31. The heating medium flowing out of the condenser bypass path 12A flows into the indoor heat exchanger 25, but the indoor air blower 25A stops working. That is, the machine room 8 is not heated. The heating medium flowing out of the indoor heat exchanger 25 returns to the evaporator 14 via the first switching valve 31 to heat the refrigerant.

[0163] Second heater mode M3-2 ( Fig.24 ): The second heater mode M3-2 is suitable for heating when the outside air temperature is significantly lower than 0°C. In the second heater mode M3 - 2 , the first refrigerant circuit R1 is used, and the series circuit CC of the heating medium circuit 20 is used.

[0164] The flow of the heating medium in the heating medium circuit 20 is different from the second heater mode M3-2 ( Figure 4 ) is the same as the flow of the heat carrier under. The terminal 24A of the outdoor heat exchanger bypass path 24-1 is similar to the fifth modification example ( Fig. 9 ) Similarly, it is arranged between the outdoor heat exchanger 23 and the first switching valve 31.

[0165] The heat medium that absorbs heat from the refrigerant in the condenser 12 flows into the indoor heat exchanger 25 to heat the interior of the machine room 8. The heat medium then flows into the evaporator 14 via the first switching valve 31 to transfer heat to the refrigerant. Thereafter, the heat medium flows into the outdoor heat exchanger bypass path 24-1 and returns to the condenser 12 via the first switching valve 31.

[0166] Direct heating 2nd heater mode M3-2-1( Fig.25 ): The direct heating second heater mode M3-2-1 is suitable for heating when the outside air temperature is significantly lower than 0°C, and the refrigerant is directly supplied to the temperature control object. In the direct heating second heater mode M3 - 2 - 1 , the first refrigerant circuit R1 and the second refrigerant circuit R2 are used, and the series circuit CC of the heating medium circuit 20 is used.

[0167] The flow of the refrigerant in the second refrigerant circuit R2 is the same as that in the cooling mode M1. The flow of the heating medium in the heating medium circuit 20 and the second heater mode M3-2 ( Fig.24 )same.

[0168] In the second heater mode M3-2 ( Fig.24 ), the air is heated only by the heating medium supplied to the indoor heat exchanger 25, and no heating medium is supplied to the refrigerant heat exchanger 14-2. According to the direct heating second heater mode M3-2-1, by supplying refrigerant to the refrigerant heat exchanger 14-2, the air can be heated by the heating medium supplied to the indoor heat exchanger 25 and the refrigerant supplied to the refrigerant heat exchanger 14-2, thereby further improving the heating capacity. Here, the refrigerant supplied to the refrigerant heat exchanger 14-2 is in a low pressure / low temperature state relative to the refrigerant in the condenser 12. However, the refrigerant supplied to the refrigerant heat exchanger 14-2 is high temperature compared to the low temperature outside air. The refrigerant supplied to the refrigerant heat exchanger 14-2 is higher in temperature than the outside air, which can be confirmed from the description of the refrigerant in the compressor heat source mode (M3-2) in paragraph

[0009] .

[0169] The temperature control system 3 may not necessarily include the heater modes M3-1 and M3-2. In this case, the temperature control system 3 may include only the operation modes (M1, M4-1, M4-2, M2) of the parallel circuits C1 and C2.

[0170] The first to fifth modifications of the first embodiment described above are also applicable to the third embodiment. The first to fifth modifications described below correspond to the modifications of the first embodiment with the same numbers.

[0171] [First Modification of the Third Embodiment] (illustration omitted) In particular, regarding the first heater mode M3-1, the temperature control system 3 may be configured in accordance with the first modification example ( Figure 5 ) Similarly, there is an indoor heat exchanger bypass path 26 for allowing the heat medium to bypass the indoor heat exchanger 25.

[0172] [Second variation of the third embodiment] (illustration omitted) In the third embodiment, also in accordance with the second modification example ( Figure 6 ) Similarly, the positions of the first pump 21 and the second pump 22 can be changed.

[0173] [Third Modification of the Third Embodiment] (illustration omitted) Furthermore, it is also possible to combine with the third modification example ( Figure 7 ) Similarly, the positions of the first pump 21 and the second pump 22 are changed.

[0174] [Fourth Modification of the Third Embodiment] (illustration omitted) The temperature control system 3 can include the fourth modification example ( Figure 8 )'s heat exchange paths 414, 415 and the battery switching valves 34, 35 have the same temperature adjustment mechanism.

[0175] [Fifth Modification of the Third Embodiment] (illustration omitted) The temperature control system 3 may also include a temperature adjustment mechanism for the battery device 6 similarly to the fourth modification example described above, and may be different from the fifth modification example ( Fig. 9) is also provided with an indoor heat exchanger bypass path 26.

[0176] [Sixth variation of the third embodiment] exist Fig.26 In the temperature control system 3-6 shown in FIG. 1 , a first switching valve 31 is disposed on the discharge side of the first pump 21 and the second pump 22. The positions of the first switching valve to the third switching valves 31 to 33 are similar to those of the third embodiment ( Figures 19 to 25 ), and is roughly turned upside down on the paper. The second switching valve 32 for switching the flow of the low-temperature heat medium is configured as a four-way valve in this modification.

[0177] [Seventh variation of the third embodiment] Two expansion valves 13-1 and 13-2 are not necessarily required. Fig. 27 As in the temperature control system 3 - 7 shown in the figure, the on-off valves 15 and 16 for switching the use of the refrigerant circuits R1 and R2 and one expansion valve 13 are provided, so that, for example, the cooling mode M1 and the first dehumidification and heating mode M4 - 1 can be operated.

[0178] From the first to seventh modified examples of the third embodiment described above, two or more can be appropriately selected and combined.

[0179] In addition to the above, the structures listed in the above embodiments may be selected or replaced, or may be appropriately changed to other structures. The temperature control system of the present invention may include other temperature control devices such as the battery device 6 in addition to or in place of the indoor heat exchanger 25 as the temperature control device. In this case, the heating medium circuit 20 includes a path for cooling or heating other temperature control devices with the heating medium.

[0180] [Note] Through the above disclosure, the structure described below will be understood. [1] A vehicle temperature control system 1-3, comprising: The refrigerant circuit 10 includes a compressor 11, a high-pressure side heat exchanger 12, a pressure reducing unit 13, and a low-pressure side heat exchanger 14, and is configured so that the refrigerant can circulate according to a refrigeration cycle; and The heating medium circuit (20) is configured to allow a heating medium for exchanging heat with the refrigerant to circulate. The heat carrier circuit 20 comprises: The high-pressure side heat exchanger 12 enables the refrigerant to exchange heat with the heat carrier; The low-pressure side heat exchanger 14 enables the refrigerant to exchange heat with the heat carrier; The outdoor heat exchanger 23 allows the external air to exchange heat with the heat carrier; The temperature control devices 6 and 25 are equivalent to the temperature control object heated or cooled by the heat carrier, or are used to heat or cool the temperature control object; An outdoor heat exchanger bypass path 24 allows the heat medium to bypass the outdoor heat exchanger 23; and The plurality of flow path switching valves 31 to 33 are configured to be able to switch the flow of the heat medium. The heat carrier circuit 20 is constructed as follows: By switching the flow of the heating medium by at least one of the plurality of flow path switching valves 31 to 33, The low-pressure side circuit C1 including the low-pressure side heat exchanger 14 and the high-pressure side circuit C2 including the high-pressure side heat exchanger 12 can be set in parallel. The structure is such that a series circuit CC including the low-pressure side heat exchanger 14 and the high-pressure side heat exchanger 12 arranged in series can be set. The temperature control system has a compressor heat source mode M3-2 as an operating mode using the series loop CC. In the compressor heat source mode M3-2, the heat carrier flowing out of the high-pressure side heat exchanger 12 flows into the low-pressure side heat exchanger 14 via the temperature control devices 6 and 25, and then flows into the high-pressure side heat exchanger 12 through the outdoor heat exchanger bypass path 24.

[0181] [2] The vehicle temperature control system according to [1], wherein: As one of the plurality of flow path switching valves 31 to 33, a two-way flow valve 31 is provided, and the two-way flow valve 31 is configured so that both the heat medium flowing out of the high-pressure side heat exchanger 12 and the heat medium flowing out of the low-pressure side heat exchanger 14 can flow. In the compressor heat source mode, the heat carrier flowing out of the high-pressure side heat exchanger 12 flows into the low-pressure side heat exchanger 14 via the two-way circulation valve 31, or bypasses the two-way circulation valve 31 and flows into the low-pressure side heat exchanger 14, and then bypasses the two-way circulation valve 31 and flows into the high-pressure side heat exchanger 12.

[0182] [3] The vehicle temperature control system according to [1] or [2], comprising: A low-pressure side bypass path 14A allows the heat medium to bypass the low-pressure side heat exchanger 14; and The low-pressure flow rate regulating valve 14V is configured to be able to adjust a flow rate ratio of the heating medium in the low-pressure heat exchanger 14 and the low-pressure bypass path.

[0183] [4] The vehicle temperature control system according to any one of [1] to [3], comprising: A high-pressure side bypass path allows the heat medium to bypass the high-pressure side heat exchanger 12; and The high-pressure side flow rate regulating valve is configured to be able to adjust the flow rate ratio of the heat medium in the high-pressure side heat exchanger 12 and the high-pressure side bypass path. The vehicle temperature control system includes a startup compressor heat source mode as an operation mode using the series circuit CC. In the compressor heat source mode at startup, the heat carrier flowing out of the high-pressure side heat exchanger 12 flows into the low-pressure side heat exchanger 14, then passes through the outdoor heat exchanger 23, and flows into the high-pressure side heat exchanger 12 and at least the high-pressure side bypass path of the high-pressure side bypass path.

[0184] [5] The vehicle temperature control system according to [4], wherein: The startup compressor heat source mode causes the heating medium flowing out of the low-pressure side heat exchanger 14 to flow into the outdoor heat exchanger 23 .

[0185] [6] The vehicle temperature control system according to [4] or [5], comprising: A temperature control bypass path 26 is provided for bypassing the heating medium from the temperature control device 25 .

[0186] [7] A vehicle temperature control system according to any one of [4] to [6], wherein: A blower 25A is provided for delivering air to the temperature control device 25. The compressor heat source mode at startup stops the blower 25A.

[0187] [8] The vehicle temperature control system according to any one of [1] to [7], comprising: A battery 6, as one of the at least one temperature-controlled objects; and The heat exchange paths 414 and 415 are configured to be able to supply the heating medium to the battery 6 .

[0188] [9] A vehicle temperature control system according to any one of [1] to [8], wherein: A blower 25A is provided for delivering air to the temperature control device 25. The temperature control device 25 has: a first heat exchanger 25-1 disposed on the upwind side of the air flow from the blower 25A and configured to allow the heating medium flowing out of the low-pressure side heat exchanger 14 to flow into the first heat exchanger 25-1; and The second heat exchanger 25 - 2 is disposed on the leeward side of the air flow, and is configured to allow the heating medium flowing out of the high-pressure side heat exchanger 12 to flow into the second heat exchanger 25 - 2 .

[0189]

[10] The vehicle temperature control system 3 according to any one of [1] to [9], wherein: The refrigerant circuit 10 includes The refrigerant heat exchanger 14-2, together with the temperature control heat exchanger 25 as the temperature control device, is used to heat or cool at least one of the more than one temperature control objects. Furthermore, the refrigerant is configured to be able to circulate through the compressor 11 , the high-pressure side heat exchanger 12 , the pressure reducing unit 13 , and the refrigerant heat exchanger 14 - 2 .

[0190]

[11] The vehicle temperature control system according to

[10] , wherein: A blower 25A is provided for delivering air to the refrigerant heat exchanger 14 - 2 and the temperature control device 25 , The refrigerant heat exchanger is arranged on the upwind side of the air flow based on the blower 25A. The temperature control device 25 is disposed on the downwind side of the air flow, and is configured to allow the heat medium flowing out of the high-pressure side heat exchanger 12 to flow into the temperature control device 25 .

[0191]

[12] The vehicle temperature control system according to

[10] or

[11] , wherein: The refrigerant circuit 10 includes: a first refrigerant circuit R1 configured such that the refrigerant can circulate through the compressor 11, the high-pressure side heat exchanger 12, the first decompression section 13-1 as the decompression section 13, and the low-pressure side heat exchanger 14; and The second refrigerant circuit R2 is configured to include a second decompression section 13 - 2 as the decompression section 13 , and the refrigerant can circulate through the compressor 11 , the high-pressure side heat exchanger 12 , the second decompression section 13 - 2 , and the refrigerant heat exchanger 14 - 2 .

[0192]

[13] The vehicle temperature control system according to

[12] , wherein: The first decompression section 13 - 1 and the second decompression section 13 - 2 both correspond to expansion valves.

[0193]

[14] The vehicle temperature control system according to

[12] or

[13] , wherein: The first decompression section 13 - 1 and the second decompression section 13 - 2 are the same decompression section.

[0194]

[15] A vehicle temperature control method, which is a vehicle temperature control method using a vehicle temperature control system, The temperature control system has: The refrigerant circuit 10 includes a compressor 11, a high-pressure side heat exchanger 12, a pressure reducing unit 13, and a low-pressure side heat exchanger 14, and is configured so that the refrigerant can circulate according to a refrigeration cycle; and The heating medium circuit (20) is configured to allow a heating medium for exchanging heat with the refrigerant to circulate. The heat carrier circuit 20 comprises: The high-pressure side heat exchanger 12 enables the refrigerant to exchange heat with the heat carrier; The low-pressure side heat exchanger 14 enables the refrigerant to exchange heat with the heat carrier; The outdoor heat exchanger 23 allows the external air to exchange heat with the heat carrier; The temperature control devices 6 and 25 are equivalent to the temperature control object heated or cooled by the heat carrier, or are used to heat or cool the temperature control object; An outdoor heat exchanger bypass path 24 allows the heat medium to bypass the outdoor heat exchanger 23; and The plurality of flow path switching valves 31 to 33 are configured to be able to switch the flow of the heat medium. The heat carrier circuit 20 is constructed as follows: By switching the flow of the heating medium by at least one of the plurality of flow path switching valves 31 to 33, The low-pressure side circuit C1 including the low-pressure side heat exchanger 14 and the high-pressure side circuit C2 including the high-pressure side heat exchanger 12 can be set in parallel. The structure is such that a series circuit CC including the low-pressure side heat exchanger 14 and the high-pressure side heat exchanger 12 arranged in series can be set. The temperature control method implements the compressor heat source mode M3-2 as the operating mode using the series loop CC. In the compressor heat source mode M3-2, the heat carrier flowing out of the high-pressure side heat exchanger 12 flows into the low-pressure side heat exchanger 14 via the temperature control devices 6 and 25, and then flows into the high-pressure side heat exchanger 12 through the outdoor heat exchanger bypass path 24. Explanation of symbols

[0195] 1, 2, 3- Temperature control system (temperature control system for vehicle), 6- Battery device (temperature control object, battery), 7- Control device, 8- Machine room, 10, 10-3- Refrigerant circuit, 11- Compressor, 12- Condenser (high-pressure side heat exchanger), 12A- Condenser bypass path (high-pressure side bypass path), 12V- Condenser flow control valve (high-pressure side flow control valve), 13- Expansion valve (pressure reducing section), 13-1- 1st expansion valve (1st pressure reducing section), 13-2- 2nd expansion valve (2nd pressure reducing section), 14, 14-1- Evaporation 14-2-refrigerant heat exchanger, 14A-evaporator bypass path (low-pressure side bypass path), 14V-evaporator flow control valve (low-pressure side flow control valve), 15, 16-on / off valve, 20-heat carrier circuit, 21-first pump, 22-second pump, 23-outdoor heat exchanger, 23A-outdoor blower, 24, 24-1-outdoor heat exchanger bypass path, 24A-terminal, 25-indoor heat exchanger (temperature control equipment, temperature control heat exchanger) 25-1-first heat exchanger, 25-2-second heat exchanger heat exchanger, 25A-indoor blower, 26-indoor heat exchanger bypass path (temperature control bypass path), 31-first switching valve (flow switching valve, two-way flow switching valve), 32-second switching valve (flow switching valve), 33-third switching valve (flow switching valve), 34-first battery switching valve, 35-second battery switching valve, 401-412-piping, 414-first heat exchange path, 414A-outward, 414B-return, 415-second heat exchange path, 415A-outward, 415B-return, 416, 4 17-piping, 501, 502-piping, C1-low-pressure side circuit, C2-high-pressure side circuit, CC-series circuit, L1-1st circuit, L2-2nd circuit, M1-cooling mode, M2-heat pump mode, M3-1-1st heater mode (compressor heat source mode at startup), M3-2 second heater mode (compressor heat source mode), M4-dehumidification and heating mode, M4-1-1st dehumidification and heating mode, M4-2-2nd dehumidification and heating mode, R1-1st refrigerant circuit, R2-2nd refrigerant circuit, U-HVAC unit.

Claims

1. A temperature control system for a vehicle, comprising: A refrigerant circuit includes a compressor, a high-pressure side heat exchanger, a pressure reducing unit, and a low-pressure side heat exchanger, and is configured so that the refrigerant can circulate according to a refrigeration cycle; and The heat medium circuit is configured to allow a heat medium for exchanging heat with the refrigerant to circulate. The heat carrier circuit comprises: The high-pressure side heat exchanger enables the refrigerant to exchange heat with the heat carrier; The low-pressure side heat exchanger enables the refrigerant to exchange heat with the heat carrier; An outdoor heat exchanger is used to exchange heat between the external air and the heat carrier; Temperature control equipment is equivalent to a temperature control object heated or cooled by a heat carrier, or is used to heat or cool the temperature control object; an outdoor heat exchanger bypass path, allowing the heat medium to bypass the outdoor heat exchanger; and A plurality of flow path switching valves are configured to be able to switch the flow of the heat medium, The heat carrier circuit is composed of: By switching the flow of the heat medium by at least one of the plurality of flow path switching valves, A low-pressure side circuit including the low-pressure side heat exchanger and a high-pressure side circuit including the high-pressure side heat exchanger can be set in parallel, The invention is configured to be able to set a series circuit including the low-pressure side heat exchanger and the high-pressure side heat exchanger arranged in series, The temperature control system has a compressor heat source mode as an operation mode using the series circuit, In the compressor heat source mode, the heat carrier flowing out of the high-pressure side heat exchanger flows into the low-pressure side heat exchanger via the temperature control device, and then flows into the high-pressure side heat exchanger through the outdoor heat exchanger bypass path.

2. The vehicle temperature control system according to claim 1, wherein: As one of the plurality of flow path switching valves, a two-way flow valve is provided, wherein the two-way flow valve is configured so that both the heat medium flowing out of the high-pressure side heat exchanger and the heat medium flowing out of the low-pressure side heat exchanger can flow. In the compressor heat source mode, The heat medium flowing out of the high-pressure side heat exchanger flows into the low-pressure side heat exchanger via the two-way flow valve, or flows into the low-pressure side heat exchanger by bypassing the two-way flow valve, and then flows into the high-pressure side heat exchanger by bypassing the two-way flow valve.

3. The vehicle temperature control system according to claim 1 or 2, comprising: A low-pressure side bypass path allows the heat medium to bypass the low-pressure side heat exchanger; and The low-pressure side flow rate regulating valve is configured to be able to adjust a flow rate ratio of the heating medium in the low-pressure side heat exchanger and the low-pressure side bypass path.

4. The vehicle temperature control system according to claim 1 or 2, comprising: A high-pressure side bypass path allows the heat medium to bypass the high-pressure side heat exchanger; and The high-pressure side flow regulating valve is configured to be able to adjust the flow ratio of the heat medium in the high-pressure side heat exchanger and the high-pressure side bypass path, The vehicle temperature control system includes a startup compressor heat source mode as an operation mode using the series circuit. In the compressor heat source mode at startup, the heat carrier flowing out of the high-pressure side heat exchanger flows into the low-pressure side heat exchanger, then passes through the outdoor heat exchanger, and flows into the high-pressure side heat exchanger and at least the high-pressure side bypass path of the high-pressure side bypass path.

5. The vehicle temperature control system according to claim 4, wherein: The startup compressor heat source mode causes the heating medium flowing out of the low-pressure side heat exchanger to flow into the outdoor heat exchanger.

6. The vehicle temperature control system according to claim 4, comprising: A temperature control bypass path is provided for bypassing the heating medium from the temperature control device.

7. The vehicle temperature control system according to claim 4, wherein: A blower is provided for delivering air to the temperature control device, The compressor heat source mode at startup stops the blower.

8. The vehicle temperature control system according to claim 1 or 2, comprising: Batteries, as one of more than one temperature-controlled objects; and The heat exchange path is configured to be able to supply the heating medium to the battery.

9. The vehicle temperature control system according to claim 1 or 2, wherein: A blower is provided for delivering air to the temperature control device, The temperature control device has: a first heat exchanger disposed on the upwind side of the air flow from the blower and configured to allow the heating medium flowing out of the low-pressure side heat exchanger to flow into the first heat exchanger; and The second heat exchanger is disposed on the leeward side of the air flow and is configured to allow the heating medium flowing out of the high-pressure side heat exchanger to flow into the second heat exchanger.

10. The vehicle temperature control system according to claim 1 or 2, wherein: The refrigerant circuit includes The refrigerant heat exchanger, together with the temperature control heat exchanger as the temperature control device, is used for heating or cooling at least one of the more than one temperature control objects. Furthermore, the refrigerant is configured to be able to circulate through the compressor, the high-pressure side heat exchanger, the pressure reducing unit, and the refrigerant heat exchanger.

11. The vehicle temperature control system according to claim 10, wherein: A blower for delivering air to the refrigerant heat exchanger and the temperature control device is provided, The refrigerant heat exchanger is arranged on the upwind side of the air flow based on the blower. The temperature control device is disposed on the leeward side of the air flow, and is configured to allow the heat medium flowing out of the high-pressure side heat exchanger to flow in.

12. The vehicle temperature control system according to claim 10, wherein: The refrigerant circuit comprises: a first refrigerant circuit configured so that the refrigerant can circulate through the compressor, the high-pressure side heat exchanger, a first decompression section as the decompression section, and the low-pressure side heat exchanger; and The second refrigerant circuit includes a second decompression section as the decompression section, and the refrigerant can circulate through the compressor, the high-pressure side heat exchanger, the second decompression section, and the refrigerant heat exchanger.

13. The vehicle temperature control system according to claim 12, wherein: The first decompression section and the second decompression section are both expansion valves.

14. A vehicle temperature control method, which is a temperature control method using a vehicle temperature control system, The temperature control system has: A refrigerant circuit includes a compressor, a high-pressure side heat exchanger, a pressure reducing unit, and a low-pressure side heat exchanger, and is configured so that the refrigerant can circulate according to a refrigeration cycle; and The heat medium circuit is configured to allow a heat medium for exchanging heat with the refrigerant to circulate. The heat carrier circuit comprises: The high-pressure side heat exchanger enables the refrigerant to exchange heat with the heat carrier; The low-pressure side heat exchanger enables the refrigerant to exchange heat with the heat carrier; An outdoor heat exchanger is used to exchange heat between the external air and the heat carrier; Temperature control equipment is equivalent to a temperature control object heated or cooled by a heat carrier, or is used to heat or cool the temperature control object; an outdoor heat exchanger bypass path, allowing the heat medium to bypass the outdoor heat exchanger; and A plurality of flow path switching valves are configured to be able to switch the flow of the heat medium, The heat carrier circuit is composed of: By switching the flow of the heat medium by at least one of the plurality of flow path switching valves, A low-pressure side circuit including the low-pressure side heat exchanger and a high-pressure side circuit including the high-pressure side heat exchanger can be set in parallel, The invention is configured to be able to set a series circuit including the low-pressure side heat exchanger and the high-pressure side heat exchanger arranged in series, The temperature control method implements a compressor heat source mode as an operation mode using the series circuit, In the compressor heat source mode, the heat carrier flowing out of the high-pressure side heat exchanger flows into the low-pressure side heat exchanger via the temperature control device, and then flows into the high-pressure side heat exchanger through the outdoor heat exchanger bypass path.

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